Inertia disc quick connecting device for marine propulsion diesel engine and gearbox

Abstract

The utility model provides a quick connecting device with an inertia disc for a marine propulsion diesel engine and a gearbox, and belongs to the technical field of diesel engines. A marine propulsion diesel engine crankshaft flange plate is in fastening connection with a rigid flywheel, the rigid flywheel is in fastening connection with a left rigid gear ring of a high-elasticity rubber coupling, and a right output shaft flange plate of the high-elasticity rubber coupling is in fastening connection with an inertia disc and a gearbox flange plate; the inertia disc is arranged between the high-elasticity rubber coupling and the gear box flange plate, and a turning gear ring is arranged on the inertia disc; the fastening connection mode of the marine propulsion diesel engine crankshaft flange plate and the rigid flywheel and the fastening connection mode of the right side output shaft flange plate of the high-elasticity rubber coupling and the inertia disc and the gearbox flange plate are in non-reamed clearance fit between the inner diameter of the through hole and the outer diameter of the non-threaded position of the stud and the bolt. According to the scheme, quick connection of the shaft system between the marine propulsion diesel engine and the gearbox and reliable and stable operation of the whole shaft system are achieved, the structure is simple, the manufacturing cost is low, and the installation efficiency is high.

Description

Technical Field

[0001] The utility model belongs to the technical field of diesel engines, and specifically relates to a quick connection device with an inertia disc for a marine propulsion diesel engine and a gear box. The quick connection device with an inertia disc and a method are used for the centering connection of the shaft system between the marine propulsion diesel engine and the gear box. Background Art

[0002] In the application field of marine propulsion diesel engines, a reduction gearbox is generally provided between the propulsion diesel engine and the propeller, and the speed of the entire shaft system can be reduced through the reduction gearbox to increase the propulsion power of the propeller. At present, a high-elastic rubber coupling + rigid flywheel connection scheme is generally used between the marine propulsion diesel engine and the gearbox. Specifically, one side of the rigid flywheel is connected to the propulsion diesel engine crankshaft flange through a through-hinged stud bolt, and the other side of the rigid flywheel is connected to the rigid gear ring of the high-elastic rubber coupling through screws, and the other side of the high-elastic coupling with the output shaft flange is directly connected to the gearbox input shaft flange through a hinged bolt. The above-mentioned high elastic rubber coupling + rigid flywheel connection scheme is usually implemented in two steps during the installation phase at the production site: ① During the manufacturing phase in the marine propulsion diesel engine factory, one side of the rigid flywheel is connected to the crankshaft flange of the propulsion diesel engine by means of through-hinged stud bolts; ② During the installation phase in the cabin outside the marine propulsion diesel engine factory, the other side of the rigid flywheel is connected to the rigid gear ring of the high elastic rubber coupling by means of screws, and the output shaft flange on the other side of the high elastic coupling is directly connected to the input shaft flange of the gearbox by means of hinged bolts.

[0003] The above high elastic rubber coupling + rigid flywheel connection scheme is divided into two installation processes during execution: the in-factory manufacturing stage of the marine propulsion diesel engine and the in-cabin installation stage outside the factory. During the installation process, the transition matching size of the reamed hole and the outer diameter of the matching bolt often exceeds the tolerance, and the on-site installation personnel are required to manually ream the connecting through-bolt hole again. This has high requirements on the operating skills of the on-site installation personnel. At the same time, the on-site installation takes a long time, resulting in low production efficiency and high labor costs for marine propulsion diesel engines. Taking the above factors into consideration, this connection scheme is not conducive to the mass production of marine propulsion diesel engines.

[0004] During the manufacturing and assembly of marine propulsion diesel engines and the subsequent installation and commissioning in the cabin, the entire shaft system needs to be turned to meet the requirements of shape and position dimension detection at different phase angles during the installation and commissioning stage. Therefore, it is necessary to install a turning gear ring structure to achieve fast and efficient response rotation of the shaft system during the installation and commissioning of the marine propulsion diesel engine. The commonly used method at present is to install a turning gear ring on the rigid flywheel. The method of installing a turning gear ring on the rigid flywheel will cause the outer diameter of the rigid flywheel to increase exponentially, and will also increase the moment of inertia on one side of the rigid flywheel. On the side of the flywheel connected to the marine propulsion diesel engine, components such as lubricating oil, fuel pipes and superchargers are usually arranged, and the installation space is limited. When installing a rigid flywheel with a gear ring, the hoisting and installation process has a narrow working space and parts often collide, which results in low installation efficiency and low reliability of installation quality; in addition, the moment of inertia on both sides of the high elastic rubber coupling of the entire shaft system is uneven, which will cause the gear meshing impact of the gearbox during operation, and the noise is large, which ultimately brings potential risks to the stable operation of the gearbox. Utility Model Content

[0005] The technical problem solved by the utility model is to provide a quick connection device with an inertia disc between a marine propulsion diesel engine and a gear box. The utility model aims to realize the quick connection of the shaft system between the marine propulsion diesel engine and the gear box and the reliable and stable operation of the entire shaft system, and to design a quick connection device with an inertia disc and a method. The utility model has a simple structural design, low processing and manufacturing costs, and high on-site installation efficiency. At the same time, it can avoid the gear meshing impact phenomenon that occurs when the gear box is running, reduce the noise generated when the gear box is running, and finally improve the stability of the operation of the entire shaft system of the marine propulsion diesel engine, laying a solid foundation for the reliable and stable operation of the gear box in the later stage.

[0006] In order to achieve the above purpose, the technical solution adopted by the utility model is:

[0007] A quick connection device with an inertia disc between a marine propulsion diesel engine and a gearbox, comprising a marine propulsion diesel engine crankshaft flange, a rigid flywheel, a high-elastic rubber coupling, an inertia disc, and a gearbox flange;

[0008] The crankshaft flange of the marine propulsion diesel engine is tightly connected to the rigid flywheel, the rigid flywheel is tightly connected to the left rigid gear ring of the high elastic rubber coupling, the right output shaft flange of the high elastic rubber coupling is tightly connected to the inertia disc and the gear box flange; the inertia disc is arranged between the high elastic rubber coupling and the gear box flange, and the inertia disc is provided with a turning gear ring;

[0009] Among them, the fastening connection method between the crankshaft flange of the marine propulsion diesel engine and the rigid flywheel, as well as the fastening connection between the right output shaft flange of the high-elastic rubber coupling and the inertia disc and the gear box flange are all non-hinge clearance fit between the inner diameter of the through hole and the outer diameter of the non-threaded part of the stud and bolt.

[0010] Further limiting the above scheme, the crankshaft flange of the marine propulsion diesel engine is fastened to the rigid flywheel through a double-headed through-hole stud, a slotted nut, and a split pin, the two slotted nuts are respectively installed on the left and right stud heads of the double-headed through-hole stud, and the split pin is respectively installed in the left and right stud head through holes of the double-headed through-hole stud;

[0011] The rigid flywheel is fastened to the left rigid gear ring of the high elastic rubber coupling via a hexagon socket screw;

[0012] The right output shaft flange of the high elastic rubber coupling is fastened to the inertia disc and the gear box flange by means of external hexagonal through-bolts with holes, anti-loosening steel wires and external hexagonal nuts, wherein the anti-loosening steel wires pass through the through holes of two groups of external hexagonal through-bolts with holes to lock them together, and the external hexagonal nuts are matched and installed at the threads of the external hexagonal through-bolts with holes in pairs of two groups;

[0013] The double-headed through-studs with holes and slotted nuts of the fasteners that centrally connect the crankshaft flange of the marine propulsion diesel engine and the rigid flywheel adopt a large torque preload; at the same time, the hexagonal through-bolts with holes and hexagonal nuts of the fasteners that centrally connect the right-side output shaft flange of the high-elasticity rubber coupling and the inertia disc and the gearbox flange also adopt a large torque preload.

[0014] Further limitation of the above scheme, the rigid flywheel is a stepped concave hollow structure, and its material is Q275A\GB / T 700-2006; specifically including threaded holes, flywheel through holes, marking hole "0", center circle through hole, center circle through hole inner surface, boss, boss end face, boss outer surface, groove, groove end face, groove outer surface, flywheel outer surface, flywheel outer surface, flywheel stop groove, flywheel stop groove outer surface, flywheel stop groove end face, flywheel outer surface hoisting tool installation hole;

[0015] Wherein, the threaded holes are provided with a plurality of holes evenly distributed on the diameter The thread type adopts GB / T193-2003 blind hole; the flywheel through hole is provided with multiple and evenly distributed on the diameter The marking hole "0" is located on the center line of the rigid flywheel in the vertical direction and is L1 away from the center point. The two ends of the center line of the marking hole "0" center line angle A1 are marked on the outer surface of the flywheel, and the two ends of the center line of the marking hole "0" center line angle A2 are marked on the outer surface of the flywheel. The top dead center mark of each cylinder stroke is used to facilitate the adjustment of the injection advance angle and the rotation phase angle of each cylinder during the installation of the marine propulsion diesel engine and the shaft system connection and centering. The center circle through hole is a rigid flywheel deweighting hole, and its diameter is The width value L4 ensures that the rigid flywheel maintains a reasonably set moment of inertia value under the existing volume. The inner surface of the center circle through hole is used as the processing reference A of the entire rigid flywheel; the boss end surface of the boss is used as the processing reference B of the entire rigid flywheel, with a surface roughness Ra=3.2um, and the boss outer diameter of the boss is The width value is L2, the angle between the outer cylindrical surface of the boss and the outer cylindrical end surface of the flywheel is rounded R3 to eliminate concentrated stress and residual stress during processing; the surface roughness of the groove end surface of the groove is Ra=3.2um, and the outer cylindrical surface diameter of the groove is The width of the groove is L5-L4-L6, and the angle between the end face of the groove and the outer cylindrical surface of the groove is rounded R1 to eliminate concentrated stress and processing residual stress; the outer cylindrical surface diameter of the flywheel is The width of the outer circumference of the flywheel and the width of the outer circumference of the boss L2 constitute the total width L3 of the rigid flywheel; the outer circumference diameter of the flywheel stop groove of the flywheel stop groove is The width is L6, and the angle between the outer cylindrical surface of the flywheel stop groove and the end face of the flywheel stop groove is chamfered R1 to eliminate concentrated stress and residual stress during processing. At the same time, the end face of the outer cylindrical surface of the flywheel stop groove is chamfered C1 to avoid scratching the surface of the part during installation; a plurality of flywheel outer cylindrical surface lifting tool installation holes are evenly distributed along the circumferential direction on the outer cylindrical surface of the rigid flywheel.

[0016] Further limiting the above scheme, the crankshaft flange of the marine propulsion diesel engine and the left rigid gear ring of the high elastic rubber coupling are respectively connected to the central circular through hole of the rigid flywheel and the stop groove of the flywheel, wherein the crankshaft flange of the marine propulsion diesel engine is in contact and fastened with the boss end face of the rigid flywheel, and the left rigid gear ring of the high elastic rubber coupling is in contact and fastened with the flywheel stop groove end face of the rigid flywheel;

[0017] The verticality of the boss end face relative to the inner circular surface reference A of the center circle through hole is 0.04mm and the surface roughness is Ra=1.6um. The coaxiality of the outer circular surface of the flywheel stop groove relative to the inner circular surface reference A of the center circle through hole is 0.05mm and the verticality of the flywheel stop groove end face relative to the inner circular surface reference A of the center circle through hole is 0.04mm. At the same time, the parallelism of the flywheel stop groove end face relative to the boss end face reference B is 0.04mm, the verticality of the boss end face reference B relative to the inner circular surface reference A of the center circle through hole is 0.04mm and the surface processing roughness is Ra=3.2um; the surface roughness of the groove end face of the groove is Ra=3.2um, and the outer circular surface diameter of the groove is The width L5-L4-L6 of the groove provides installation space for fastening the double-headed through-hole stud, slotted nut and cotter pin on one side of the rigid flywheel; the aperture size of the flywheel through hole of the rigid flywheel is greater than or equal to the outer diameter size of the double-headed through-hole stud and forms a small clearance fit.

[0018] Further limiting the above scheme, the inertia disc is a stepped concave-convex hollow structure, and its material is Q275A\GB / T 700-2006; specifically including a disc through hole, a disc hoisting hole, a center weight-removing through hole, an inner circle of the center weight-removing through hole, a stop boss, an outer circle of the stop boss, a disc stop groove, a disc stop groove end face, an inertia disc step circle surface weight-removing hole, an inertia disc circle end face, an inertia disc step circle, and an inertia disc gear ring;

[0019] The disc through holes are provided with a plurality of holes evenly distributed on the diameter The base circle of the disk is provided with two hoisting holes and arranged symmetrically along the central axis. The angle between the hoisting hole of the disk and the vertical center line of the inertia disk is B11. The two hoisting holes of the disk are distributed in the diameter The center de-weighting through hole includes an inner circle of the center de-weighting through hole, and the diameter of the inner circle of the center de-weighting through hole is The inner surface of the central through hole is used as the processing reference A of the entire inertia disk, and the surface roughness Ra=1.6um; the stop boss includes a stop boss outer circle, the length of the stop boss is L13, and the outer diameter size of the stop boss outer circle is The disc stop groove includes a disc stop groove end surface, and the diameter of the disc stop groove is The depth is L15-L14; the plurality of deweighting holes on the step circular surface of the inertia disc are evenly distributed along the outer circumference of the step circular surface of the inertia disc, and the distance between the center line of the deweighting hole on the step circular surface of the inertia disc and the left end surface of the step circular surface of the inertia disc is L11. At the same time, the deweighting hole on the step circular surface of the inertia disc is arranged together with the central deweighting through hole as an auxiliary deweighting hole to ensure that the entire inertia disc maintains a reasonable set value of the moment of inertia; the end surface of the inertia disc is used as the processing reference B of the entire inertia disc, and the surface roughness Ra=3.2um; the inertia disc gear ring adopts an integrated processing method with the inertia disc, and the tooth shape of the inertia disc gear ring adopts a standard involute straight tooth, with the number of teeth Z=110, the pressure angle a=20°, the module m=10, the pitch circle diameter d=1100mm, and the length of the common normal line across 13 teeth The tooth root fillet radius r′=0.5mm, and the processing accuracy is implemented in accordance with GB / T10095.2-2008-Q9; the chamfer R4 at the angle between the inertia disc step circle and the inertia disc gear ring can eliminate the concentrated stress at the root of the inertia disc gear ring during operation and the residual stress in the processing process; the outer circular end surface of the stop boss is chamfered R5 at the right angle.

[0020] Further definition of the above scheme, the right side output shaft flange of the high elastic rubber coupling is connected to the stop boss on the left side of the inertia disc, and the stop groove on the right side of the inertia disc is connected to the gear box flange; wherein, the groove surface of the right side output shaft flange of the high elastic rubber coupling is in contact and fastened with the end face of the stop boss on the left side of the inertia disc and the circular end face of the inertia disc, and the end face of the disc stop groove to which the disc stop groove on the right side of the inertia disc belongs is in contact and fastened with the gear box flange; the end face of the disc stop groove is relative to the inner circular surface of the center circular through hole The verticality of the processing datum A is 0.02mm, the parallelism of the end face of the disc stop groove relative to the processing datum B of the inertia disc circular end face is 0.15mm, and the surface roughness of the inner circle processing datum A of the center weight-removing through hole is Ra=1.6um, the surface roughness of the end face of the disc stop groove is Ra=3.2um, and the surface roughness of the inertia disc circular end face processing datum B is Ra=3.2um. At the same time, the coaxiality of the outer circle of the stop boss relative to the inner circle processing datum A of the center weight-removing through hole is 0.04mm; the diameter of the stop boss on the left side of the inertia disc is The diameter of the disc stop groove on the right side of the inertia disc is smaller than the inner diameter of the output shaft flange on the right side of the high elastic rubber coupling. The size is larger than the outer diameter of the gear box flange, and the above-mentioned matching dimensions are all clearance fits; the right-side output shaft flange of the high-elastic rubber coupling is fastened with the inertia disk and the gear box flange by multiple groups of circumferentially evenly distributed external hexagonal through bolts with holes, anti-loosening wires, and external hexagonal nuts, and the outer diameter of the external hexagonal through bolts with holes is smaller than the inner diameter of the connecting holes of the right-side output shaft flange of the high-elastic rubber coupling, the through holes of the inertia disk, and the connecting holes of the gear box flange; in addition, two external hexagonal nuts in each group are distributed on one side of the right-side output shaft flange of the high-elastic rubber coupling, and the two external hexagonal nuts are pre-tightened on the threads of the external hexagonal through bolts with holes in succession, and the anti-loosening wires are distributed on the hexagonal positions of the holes of the external hexagonal through bolts on one side of the gear box flange, and each group of two external hexagonal through bolts with holes are locked together at the same time.

[0021] The advantages of this utility model compared with the prior art:

[0022] 1. This solution solves the problem of quick centering connection of the shaft system between the marine propulsion diesel engine and the gearbox, while improving the reliability and stability of the entire shaft system operation;

[0023] 2. The overall structure of this scheme is simple and safe. The high-elastic rubber coupling has a three-stage distribution design on both sides. The fastening connection is stable and reliable. Both sides are connected by non-hinge hole studs and bolts. The on-site installation is convenient and fast, the installation skills are low, the processing and manufacturing costs are low, and it is conducive to mass production.

[0024] 3. In this scheme, the rigid flywheel and the inertia disc are arranged on the left and right sides of the high elastic rubber coupling, so that the rotational inertia on both sides of the high elastic rubber coupling is evenly distributed, which solves the problem of severe gear meshing impact and high noise in the gearbox during the operation of the shaft system of the previous marine propulsion diesel engine, and improves the service life and working performance of the gearbox;

[0025] 4. This solution can be applied to the quick connection of various types of marine propulsion diesel engines and gearbox shaft alignment;

[0026] 5. This solution has a simple and reliable structure, is convenient for on-site installation and has high efficiency. After two stages of on-site installation verification in the manufacturing plant and in the cabin, the shaft alignment work can be completed in a total of 4 to 6 hours;

[0027] 6. This solution is versatile and adaptable, can meet the requirements of mass production, and has good practical application effects and promotion value in the field of centering and connecting the shafting of marine propulsion diesel engines and gearboxes. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 It is a schematic diagram of the overall structure of the utility model.

[0029] Figure 2 This is a structural front view of the rigid flywheel in the utility model;

[0030] Figure 3 For this utility model Figure 2 BB structural diagram of the rigid flywheel shown in;

[0031] Figure 4 For this utility model Figure 3 The enlarged structural diagram of the C part shown in FIG.

[0032] Figure 5 This is a structural front view of the inertia disc in the utility model;

[0033] Figure 6 For this utility model Figure 5 Schematic diagram of the DD direction structure of the inertia disk shown in. DETAILED DESCRIPTION

[0034] The following will be combined with the drawings in the embodiments of the utility model to clearly and completely describe the technical solutions in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments of the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0035] It should be noted that, in this article, the terms "include", "comprises" or any other variations thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also includes other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by the sentence "includes a ..." does not exclude the presence of other identical elements in the process, method, article or device including the element.

[0036] See also Figure 1-6 , describe the embodiments of the present utility model in detail.

[0037] Embodiment: A quick connection device with an inertia disc for a marine propulsion diesel engine and a gearbox comprises a marine propulsion diesel engine crankshaft flange 1, a rigid flywheel 5, a highly elastic rubber coupling 6, an inertia disc 8, and a gearbox flange 9.

[0038] The marine propulsion diesel engine crankshaft flange 1 is tightly connected to the rigid flywheel 5, the rigid flywheel 5 is tightly connected to the left rigid gear ring 6-1 of the high elastic rubber coupling 6, the right output shaft flange 6-2 of the high elastic rubber coupling 6 is tightly connected to the inertia disc 8 and the gear box flange 9; the inertia disc 8 is arranged between the high elastic rubber coupling 6 and the gear box flange 9, and at the same time, the inertia disc 8 is provided with a turning gear ring.

[0039] Among them, the fastening connection mode of the crankshaft flange 1 of the marine propulsion diesel engine and the rigid flywheel 5, and the fastening connection of the right output shaft flange 6-2 of the high elastic rubber coupling 6 and the inertia disc 8 and the gear box flange 9 are all non-reamed clearance matching between the inner diameter of the through hole and the outer diameter of the non-threaded part of the stud and bolt. This connection structure avoids the problem of transition matching tolerance between the reamed hole and the outer diameter of the matching bolt that often occurs during on-site installation, requiring on-site installation personnel to manually re-ream the connecting through bolt hole, and has low requirements on the operating skills of on-site installation personnel, high on-site installation efficiency, and is conducive to the mass production and manufacturing of marine propulsion diesel engines.

[0040] In this embodiment, the structure is simple and safe, the left and right sides of the high elastic rubber coupling 6 are both three-stage distribution design, the fastening connection is stable and reliable, and the left and right sides are both non-reamed hole studs and bolt connections, the on-site installation is convenient and fast, the installation skill requirements are low, the processing and manufacturing costs are low, and it is conducive to mass production and manufacturing; the inertia disc 8 is arranged between the high elastic rubber coupling 6 and the gear box flange 9, and the inertia disc 8 is provided with a turning gear ring, which eliminates the problem of the rigid flywheel outer diameter size doubling and the rigid flywheel rotational inertia increasing after the turning gear ring is added to the rigid flywheel in the past, and solves the problems of small installation working space and frequent parts collision after the traditional rigid flywheel is added with the turning gear ring, and the on-site installation efficiency is high and the installation quality reliability is stable; in addition, the rigid flywheel 5 and the inertia disc 8 are arranged on the left and right sides of the high elastic rubber coupling 6, so that the rotational inertia on both sides of the high elastic rubber coupling 6 is evenly distributed, which solves the problem of severe meshing impact and high noise in the gear box during the operation of the shaft system of the marine propulsion diesel engine in the past, and improves the service life and working performance of the gear box.

[0041] In a specific embodiment, the marine propulsion diesel engine crankshaft flange 1 is fastened to the rigid flywheel 5 through a double-headed holed through stud 2, a slotted nut 3, and a cotter pin 4. The two slotted nuts 3 are respectively installed in the left and right stud heads of the double-headed holed through stud 2, and the cotter pin 4 is respectively installed in the left and right stud head through holes of the double-headed holed through stud 2.

[0042] The rigid flywheel 5 is fastened to the rigid gear ring 6 - 1 on the left side of the highly elastic rubber coupling 6 by means of a hexagon socket screw 7 .

[0043] The right output shaft flange 6-2 of the highly elastic rubber coupling 6 is fastened to the inertia disc 8 and the gear box flange 9 by means of external hexagonal through-bolts 10, anti-loosening steel wires 11 and external hexagonal nuts 12, wherein the anti-loosening steel wires 11 pass through the through holes of two groups of external hexagonal through-bolts 10 to lock them together, and the external hexagonal nuts 12 are installed on the threads of the external hexagonal through-bolts 10 in pairs of two groups.

[0044] In the above structure, the marine propulsion diesel engine crankshaft flange 1 and the rigid flywheel 5 are fastened and connected by multiple sets of double-headed through-hole studs 2, slotted nuts 3 and cotter pins 4 evenly distributed around the circumference. The preload distribution of the contact surface between the slotted nut 3 and the marine propulsion diesel engine crankshaft flange 1 and the rigid flywheel 5 is even, and the cotter pin 4 can prevent the slotted nut 3 from loosening and falling off during rotation, so the use is safe and reliable, and the service life is long; the right output shaft flange 6-2 of the high elastic rubber coupling 6 and the inertia disc 8 and the gear box flange 9 are connected by multiple sets of external hexagonal through-hole bolts evenly distributed around the circumference. 10, anti-loosening steel wire 11, and hexagonal nut 12 are fastened together, the hexagonal through bolt with hole 10 and the hexagonal nut 12 are respectively evenly distributed on the contact surfaces of the right output shaft flange 6-2 of the high-elastic rubber coupling 6 and the gear box flange 9, and the anti-loosening steel wire 11 passes through the through holes of two groups of hexagonal through bolts with holes 10 to lock them together, and every two groups of hexagonal nuts 12 are matched and installed on the threads of the hexagonal through bolts with holes 10 to prevent the hexagonal through bolts with holes 10 from loosening and falling off during rotation. They are also safe and reliable to use and have a long service life.

[0045] In a specific implementation: see Figure 2 and 3 As shown, the rigid flywheel 5 is a stepped concave hollow structure, and its material is Q275A\GB / T 700-2006, which has high yield strength, good rigidity, convenient processing and low cost. Specifically, it includes a threaded hole 5-1, a flywheel through hole 5-2, a marking hole "0" 5-3, a center circle through hole 5-4, an inner circular surface of the center circle through hole 5-4-1, a boss 5-5, a boss end face 5-5-1, a boss outer circular surface 5-5-2, a groove 5-6, a groove end face 5-6-1, a groove outer circular surface 5-6-2, a flywheel outer circular surface 5-7, a flywheel outer circular end face 5-8, a flywheel stop groove 5-9, a flywheel stop groove outer circular surface 5-9-1, a flywheel stop groove end face 5-9-2, and a flywheel outer circular surface hoisting tool installation hole 5-10.

[0046] The number of threaded holes 5-1 is 32 and they are evenly distributed on the diameter The thread type adopts GB / T193-2003 blind hole; the flywheel through holes 5-2 are 8 in number and evenly distributed on the diameter The marking hole "0" 5-3 is located on the center line of the rigid flywheel 5 in the vertical direction and is L1 away from the center point. Taking a certain type of 8-cylinder marine propulsion diesel engine as an example, the two ends of the center line of the angle A1 with the marking hole "0" 5-3 center line are marked on the outer surface 5-7 of the flywheel 3, 6TDC, 4, 5DCT, and the two ends of the center line of the angle A2 with the marking hole "0" 5-3 center line are marked on the outer surface 5-7 of the flywheel 1, 8TDC, 2, 7DCT. The above-mentioned top dead center marks of each cylinder stroke 3, 6TDC, 4, 5DCT, 1, 8TDC, 2, 7DCT are used to adjust the injection advance angle and the rotation phase angle of each cylinder during the installation of the marine propulsion diesel engine and the shaft system connection centering; the center circle through hole 5-4 is a weight removal hole of the rigid flywheel 5, and its diameter is The width value L4 ensures that the rigid flywheel 5 maintains a reasonably set moment of inertia value under the existing volume. The inner circular surface 5-4-1 of the center circle through hole is used as the processing reference A of the entire rigid flywheel 5; the boss end surface 5-5-1 of the boss 5-5 is used as the processing reference B of the entire rigid flywheel 5, and the surface roughness Ra=3.2um. The boss outer circular surface 5-5-2 of the boss 5-5 has a diameter of The width value is L2, the angle between the boss outer cylindrical surface 5-5-2 and the flywheel outer cylindrical end surface 5-8 is rounded R3 to eliminate concentrated stress and processing residual stress; the surface roughness Ra of the groove end surface 5-6-1 of the groove 5-6 is 3.2um, and the diameter of the groove outer cylindrical surface 5-6-2 of the groove 5-6 is The width of the groove 5-6 is L5-L4-L6, and the angle between the groove end surface 5-6-1 and the groove outer cylindrical surface 5-6-2 is rounded R1 to eliminate concentrated stress and processing residual stress; the diameter of the flywheel outer cylindrical surface 5-7 is The width of the flywheel outer surface 5-7 and the width L2 of the boss outer surface 5-5-2 constitute the total width L3 of the rigid flywheel 5; the diameter of the flywheel stop groove outer surface 5-9-1 of the flywheel stop groove 5-9 is The width is L6, and the angle between the outer cylindrical surface 5-9-1 of the flywheel stop groove and the end surface 5-9-2 of the flywheel stop groove is chamfered R1 to eliminate concentrated stress and residual stress during processing. At the same time, the end surface of the outer cylindrical surface 5-9-1 of the flywheel stop groove is chamfered C1 to avoid scratching the surface of the part during installation and improve installation efficiency. Eight flywheel outer cylindrical surface lifting tool installation holes 5-10 are evenly distributed along the circumferential direction on the flywheel outer cylindrical surface 5-7 of the rigid flywheel 5 to ensure that the rigid flywheel 5 is safely and firmly clamped by the lifting tool during installation, and at the same time, the manual crowbar turning installation hole function can be provided during the in-plant manufacturing stage of the marine propulsion diesel engine.

[0047] See also Figure 1 -- Figure 4As shown, the marine propulsion diesel engine crankshaft flange 1 and the left rigid gear ring 6-1 of the high elastic rubber coupling 6 are respectively connected to the central circular through hole 5-4 of the rigid flywheel 5 and the flywheel stop groove 5-9, wherein the marine propulsion diesel engine crankshaft flange 1 is in contact and fastened with the boss end face 5-5-1 of the rigid flywheel 5, and the left rigid gear ring 6-1 of the high elastic rubber coupling 6 is in contact and fastened with the flywheel stop groove end face 5-9-2 of the rigid flywheel 5;

[0048] The verticality of the boss end face 5-5-1 relative to the inner circular surface 5-4-1 of the center circle through hole datum A is 0.04mm and the surface roughness is Ra=1.6um, the coaxiality of the outer circular surface 5-9-1 of the flywheel stop groove relative to the inner circular surface 5-4-1 of the center circle through hole datum A is 0.05mm and the verticality of the flywheel stop groove end face 5-9-2 relative to the inner circular surface 5-4-1 of the center circle through hole datum A is 0.04mm, and at the same time, the parallelism of the flywheel stop groove end face 5-9-2 relative to the boss end face 5-5-1 datum B is 0.04mm, the verticality of the boss end face 5-5-1 datum B relative to the inner circular surface 5-4-1 of the center circle through hole datum A is 0.04mm and the surface processing roughness is Ra=3.2um. The machining shape and position tolerance requirements corresponding to the boss end face 5-5-1, the inner circular surface 5-4-1 of the center circle through hole, the outer circular surface 5-9-1 of the flywheel stop groove, and the end face 5-9-2 of the flywheel stop groove in the rigid flywheel 5 improve the shape and position accuracy of the centering connection between the marine propulsion diesel engine crankshaft flange 1, the left rigid gear ring 6-1 of the high elastic rubber coupling 6 and the rigid flywheel 5 and the reliability of the fastening connection. At the same time, the contact force between the contact surfaces is evenly distributed, ensuring that no slip occurs between the contact fastening surfaces during the rotation of the entire shaft system. The flywheel stop groove 5-9 plays a centering guide role, which improves the centering connection operation efficiency between the rigid flywheel 5 and the left rigid gear ring 6-1 of the high elastic rubber coupling 6.

[0049] The surface roughness of the groove end surface 5-6-1 of the groove 5-6 is Ra=3.2um, and the diameter of the groove outer surface 5-6-2 of the groove 5-6 is The width L5-L4-L6 of the groove 5-6 provides installation space for the through-hole double-headed stud 2, the slotted nut 3, and the cotter pin 4 to be fastened and connected on one side of the rigid flywheel 5, avoiding interference with the position of the rigid gear ring 6-1 on the left side of the highly elastic rubber coupling 6. At the same time, the slotted nut 3 and the groove end face 5-6-1 are fastened and contacted, the bolt preload is evenly distributed between the contact surfaces, the fit between the contact surfaces is high, the connection is reliable, and the service life is long. In addition, the aperture size of the flywheel through hole 5-2 of the rigid flywheel 5 is greater than or equal to the outer diameter size of the through-hole double-headed stud 2 to form a small clearance fit, which can realize the fast fastening connection between the through-hole double-headed stud 2, the slotted nut 3, and the cotter pin 4 of the rigid flywheel 5 and the rigid gear ring 6-1 on the left side of the highly elastic rubber coupling 6, thereby improving the efficiency of on-site installation operations.

[0050] In a specific implementation: see Figure 5 , Figure 6 As shown, the inertia disc 8 is a stepped concave-convex hollow structure, and its material is Q275A\GB / T 700-2006, which has high yield strength, good rigidity, convenient processing and low cost. Specifically, it includes a disc through hole 8-1, a disc hoisting hole 8-2, a center weight-removing through hole 8-3, an inner circle of the center weight-removing through hole 8-3-1, a stop boss 8-4, an outer circle of the stop boss 8-4-1, a disc stop groove 8-5, a disc stop groove end face 8-5-1, an inertia disc step circle surface weight-removing hole 8-6, an inertia disc circle end face 8-7, an inertia disc step circle 8-8, and an inertia disc gear ring 8-9.

[0051] The number of the disc through holes 8-1 is 16 and is evenly distributed on the diameter The base circle; the disc hoisting hole 8-2 is provided with 2 and is symmetrically arranged about the central axis, the disc hoisting hole 8-2 and the vertical center line angle of the inertia disc 8 is B11, and the 2 disc hoisting holes 8-2 are distributed in the diameter The arrangement of the hoisting holes 8-2 is conducive to the uniform distribution of the moment of inertia of the entire inertia disc 8 during operation and provides a suitable hoisting position for the rapid installation of the inertia disc 8. The central de-weighting through hole 8-3 includes a central de-weighting through hole inner circle 8-3-1, and the diameter of the central de-weighting through hole inner circle 8-3-1 is It can ensure that the inertia disk 8 maintains a reasonably set moment of inertia value under the existing volume; the inner circle 8-3-1 of the center weight-removing through hole is used as the processing reference A of the entire inertia disk 8, and the surface roughness Ra=1.6um; the stop boss 8-4 includes a stop boss outer circle 8-4-1, the length of the stop boss 8-4 is L13, and the outer circle diameter size of the stop boss outer circle 8-4-1 is The disk stop groove 8-5 includes a disk stop groove end surface 8-5-1, and the diameter of the disk stop groove 8-5 is The depth is L15-L14; the 8 inertia disc step circular surface deweighting holes 8-6 are along the outer diameter of the inertia disc step circle 8-8 The center line of the inertia disc step circular surface deweighting hole 8-6 is at a distance of L11 from the left end face of the inertia disc step circle 8-8. At the same time, the inertia disc step circular surface deweighting hole 8-6 is arranged together with the central deweighting through hole 8-3 as an auxiliary deweighting hole to ensure that the entire inertia disc 8 maintains a reasonable set value of the moment of inertia; the inertia disc circular end surface 8-7 is used as the processing reference B of the entire inertia disc 8, and the surface roughness Ra=3.2um; the inertia disc gear ring 8-9 is processed in an integrated manner with the inertia disc 8, which has a compact structure, saves installation time inside the cabin, and has reliable and safe structural performance; the inertia disc gear ring 8-9 tooth shape adopts standard involute straight teeth, with the number of teeth Z=110, pressure angle a=20°, module m=10, pitch circle diameter d=1100mm, and span 13 teeth common normal length The tooth root fillet radius r'=0.5mm, the processing accuracy is implemented in accordance with GB / T10095.2-2008-Q9, and the entire inertia disc gear ring 8-9 has high transmission efficiency, convenient processing and low cost. The rounded corner R4 at the angle between the inertia disc step circle 8-8 and the inertia disc gear ring 8-9 can eliminate the concentrated stress at the root of the inertia disc gear ring 8-9 during work and the residual stress during processing, thereby improving the tooth root strength of the inertia disc gear ring 8-9; the rounded corner R5 at the right angle of the end face of the stop boss outer circle 8-4-1 can avoid scratching the surface of the matching parts during installation, improve installation efficiency, and also eliminate stress concentration and improve the overall structural strength of the inertia disc 8.

[0052] See also Figure 1 , Figure 5 , Figure 6As shown, the right side output shaft flange 6-2 of the high elastic rubber coupling 6 is connected to the stop boss 8-4 on the left side of the inertia disc 8 in an aligned manner, and the stop groove 8-5 on the right side of the inertia disc 8 is connected to the gear box flange 9 in an aligned manner; wherein, the groove surface of the right side output shaft flange 6-2 of the high elastic rubber coupling 6 is in contact and fastened with the end face inertia disc circular end face 8-7 of the stop boss 8-4 on the left side of the inertia disc 8, and the disc stop groove end face 8-5-1 to which the disc stop groove 8-5 on the right side of the inertia disc 8 belongs is in contact and fastened with the gear box flange 9; the disc stop groove end face 8-5-1 is deviated relative to the center. The verticality of the processing datum A of the inner circle 8-3-1 of the heavy through hole is 0.02mm, the parallelism of the end face 8-5-1 of the disk stop groove relative to the processing datum B of the inertia disk circular end face 8-7 is 0.15mm, and the surface roughness of the processing datum A of the inner circle 8-3-1 of the center de-weighting through hole 8-3-1 is Ra=1.6um, the surface roughness of the end face 8-5-1 of the disk stop groove is Ra=3.2um, and the surface roughness of the processing datum B of the inertia disk circular end face 8-7 is Ra=3.2um. At the same time, the coaxiality of the outer circle 8-4-1 of the stop boss relative to the processing datum A of the inner circle 8-3-1 of the center de-weighting through hole is 0.04mm.

[0053] The machining shape and position tolerance values ​​and surface roughness value requirements corresponding to the inner circle 8-3-1 of the center weight-reducing through hole, the end face 8-5-1 of the stop groove, the outer circle 8-4-1 of the stop boss, and the circular end face 8-7 of the inertia disk 8 in the above-mentioned inertia disk 8 can improve the shape and position accuracy and the reliability of the fastening connection between the right-side output shaft flange 6-2 of the high-elastic rubber coupling 6 and the stop boss 8-4 on the left side of the inertia disk 8, and the stop groove 8-5 on the right side of the inertia disk 8 and the gear box flange 9. At the same time, the contact stress between the contact surfaces is evenly distributed, ensuring that no slippage occurs between the contact fastening surfaces during the rotation of the entire shaft system. The stop groove 8-5 and the stop boss 8-4 act as a centering guide, which improves the installation efficiency of the centering connection between the output shaft flange 6-2 on the right side of the high-elasticity rubber coupling 6 and the stop boss 8-4 on the left side of the inertia disc 8, and the centering connection between the stop groove 8-5 on the right side of the inertia disc 8 and the gear box flange 9, while also ensuring the centering accuracy of the above parts after installation.

[0054] The diameter of the stop boss 8-4 on the left side of the inertia disc 8 The inner diameter of the output shaft flange 6-2 on the right side of the high elastic rubber coupling 6 is smaller than the inner diameter of the disk stop groove 8-5 on the right side of the inertia disk 8. The size is larger than the outer diameter of the gearbox flange 9, and the above-mentioned matching dimensions are clearance matching, which can avoid the problem of position interference between parts during installation, and at the same time meet the requirements of rapid guiding and positioning. The right output shaft flange 6-2 of the high elastic rubber coupling 6, the inertia disc 8, and the gearbox flange 9 are fastened and connected by multiple groups of circumferentially evenly distributed external hexagonal through-bolts 10, anti-loosening wires 11, and external hexagonal nuts 12, and the outer diameter of the external hexagonal through-bolts 10 is smaller than the connection hole of the right output shaft flange 6-2 of the high elastic rubber coupling 6, the through hole 8-1 of the inertia disc 8, and the inner diameter of the connection hole of the gearbox flange 9; it can meet the requirements of rapid through-type fastening connection between the above three, and ultimately improve the on-site installation efficiency in the cabin outside the manufacturing plant, while reducing the operating skill requirements of the on-site installation personnel, and avoiding the on-site manual reaming repair problem caused by the excessive clearance of the transition matching of the reaming hole bolt connection. In addition, two external hexagonal nuts 12 are distributed in each group on one side of the output shaft flange 6-2 on the right side of the high elastic rubber coupling 6, and the two external hexagonal nuts 12 are pre-tightened on the threads of the external hexagonal through-bolts 10 with holes in succession, and the anti-loosening steel wires 11 are distributed on the hexagonal positions of the holes of the external hexagonal through-bolts 10 on one side of the gear box flange 9, and each group of two external hexagonal through-bolts 10 are locked together at the same time. By adopting the above-mentioned two-way anti-loosening design, the problem of fastener loosening during the rotation process after the high elastic rubber coupling 6 right side output shaft flange 6-2 is quickly penetrated and fastened with the inertia disc 8 and the gear box flange 9 can be avoided, thereby improving the reliability and safety of the above-mentioned connecting parts during operation.

[0055] In a specific implementation manner: after the rigid flywheel 5 and the inertia disc 8 are machined, stress relief annealing is performed to eliminate the residual internal stress in the internal structures of the rigid flywheel 5 and the inertia disc 8 after machining, and at the same time reduce the restraint and rigidity of the rigid flywheel 5 and the inertia disc 8 to improve the stability of their processing dimensions. Finally, the centering accuracy of the rigid flywheel 5 and the inertia disc 8 after installation and tightening can be improved to ensure the reliability and safety of the entire quick connection device with the inertia disc during operation.

[0056] In a specific embodiment, the double-headed through-hole stud 2 and slotted nut 3 of the fasteners that are centrally connected between the crankshaft flange 1 of the marine propulsion diesel engine and the rigid flywheel 5 adopt a large torque preload, and at the same time, the fasteners that are centrally connected between the right output shaft flange 6-2 of the high elastic rubber coupling 6 and the inertia disc 8 and the gearbox flange 9 also adopt a large torque preload. The specific values ​​are that the preload of the double-headed through-hole stud 2 and the slotted nut 3 is 1500N.m, and the preload of the through-hole stud 10 and the hexagonal nut 12 is 2000N.m. The use of a large torque preload can make the contact stress between the contact surfaces of the marine propulsion diesel engine crankshaft flange 1, the rigid flywheel 5 and the slotted nut 3 offset the torsional stress generated during the working process between the above two, avoid sliding displacement of the contact surface between the two, and ensure the reliability and safety of the structure during the working process after the marine propulsion diesel engine crankshaft flange 1 and the rigid flywheel 5 are aligned and connected. Similarly, the use of a large torque preload can make the contact stress between the surfaces of the right output shaft flange 6-2 of the high elastic rubber coupling 6, the inertia disc 8, the gearbox flange 9 and the fasteners hexagonal through-bolts 10 and the hexagonal nuts 12 contact each other, which can resist the torsional stress generated during the working process between the above three, avoid sliding displacement of the contact surface between the three, and ensure the reliability and safety of the structure during the working process after the right output shaft flange 6-2 of the high elastic rubber coupling 6, the inertia disc 8, and the gearbox flange 9 are aligned and connected.

[0057] The actual working torsional load, bolt preload, rotational speed and other boundary conditions of the quick connection device with inertia disc are simulated, and the finite element statics and dynamic modal simulation calculations of the quick connection device with inertia disc are carried out. The results show that the structural design of the quick connection device with inertia disc is reasonable, safe and reliable, and the static strength and stiffness of the structure meet the requirements. At the same time, the modal vibration shape of the quick connection device with inertia disc can avoid the resonance range, and no resonance will occur during the working process.

[0058] In the above embodiments, They are all diameter codes, not specific diameter parameters.

[0059] A method for assembling a quick connection device with an inertia disc between a marine propulsion diesel engine and a gearbox comprises the following steps:

[0060] Step a: installing the rigid flywheel 5 during the manufacturing stage in the marine propulsion diesel engine factory, and visually inspecting before installation to ensure that the stopper surface and the joint surface between the marine propulsion diesel engine crankshaft flange 1 and the rigid flywheel 5 are free of burrs and high points;

[0061] Step b: Install a simple manual turning tool on the marine propulsion diesel engine crankshaft flange 1, manually turn the marine propulsion diesel engine to the first cylinder close to the upper dead center of the marine propulsion diesel engine crankshaft flange 1, then install the lifting clamping tool on the flywheel outer cylindrical surface lifting tool installation hole 5-10 of the rigid flywheel 5, and then lift the rigid flywheel 5 to a proper distance from the marine propulsion diesel engine crankshaft flange 1, visually align the marking hole "0" 5-3 of the rigid flywheel 5 with the corresponding mark on the marine propulsion diesel engine crankshaft flange 1, and quickly install the rigid flywheel 5 on the end of the marine propulsion diesel engine crankshaft flange 1 through the stopper positioning;

[0062] Step c: Pass eight double-headed through-hole studs 2 through the flywheel through hole 5-2 of the rigid flywheel 5 and the flange hole of the marine propulsion diesel engine crankshaft flange 1 at the same time, and the threaded parts of the double-headed through-hole studs 2 exposed on both sides of the rigid flywheel 5 and the marine propulsion diesel engine crankshaft flange 1 are of equal length. Install a slotted nut 3 on both sides of the exposed threaded part of each double-headed through-hole stud 2, tighten the slotted nuts 3 on both sides with a torque wrench, and align the open grooves of the slotted nuts 3 on both sides with the cotter pin holes of the threaded parts on both sides of the double-headed through-hole studs 2, and ensure that the tightening torque is not less than 1500N.m. Finally, install the cotter pins 4 in the cotter pin holes of the threaded parts on both sides of each double-headed through-hole stud 2 to lock each corresponding slotted nut 3.

[0063] Step d: Install the high elastic rubber coupling 6 and the inertia disc 8 during the installation stage in the cabin outside the ship propulsion diesel engine factory. Before installation, confirm that the stop surfaces and joint surfaces between the connecting parts are free of burrs and high points. At the same time, measure the axial spacing La from the flywheel stop groove end face 5-9-2 of the rigid flywheel 5 to the gear box flange 9 end face, and ensure that La = Lb ± 0.6mm. Among them, Lb is the theoretical assembly spacing, Lb = Lc + Ld; Lc is the axial distance from the left rigid gear ring 6-1 boss surface of the high elastic rubber coupling 6 to the right output shaft flange 6-2 groove surface; Ld is the axial distance L14 of the inertia disc 8.

[0064] Step e: disassemble the left rigid gear ring 6-1 from the high-elastic rubber coupling 6, mark the positions of the removed bolts for subsequent reinstallation; use a hoist to lift the left rigid gear ring 6-1 to an appropriate position, quickly install the boss surface of the left rigid gear ring 6-1 in the flywheel stop groove 5-9 of the rigid flywheel 5 through the stop positioning, then use 32 hexagon socket screws 7 to fasten the left rigid gear ring 6-1 to the rigid flywheel 5, and finally use a torque wrench to tighten it according to the required torque.

[0065] Step f: Use a lifting device to lift the inertia disc 8 to a suitable position away from the gear box flange 9, and quickly install one side of the disc stop groove end face 8-5-1 of the inertia disc 8 on the gear box flange 9 through the stop positioning, and insert two tooling support rods in the horizontal and vertical directions through the bolt holes on one side of the gear box flange 9, and ensure that the end face of the tooling support rod does not expose the inertia disc circular end face 8-7 on the left side of the inertia disc 8.

[0066] Step g: Use a lifting device to lift the high elastic rubber coupling 6 without the left rigid gear ring 6-1 to a proper position, align the stop groove of the right output shaft flange 6-2 of the high elastic rubber coupling 6 with the stop boss 8-4 on the left side of the inertia disc 8, and quickly insert 12 external hexagonal through bolts 10 through the bolt holes on one side of the gear box flange 9 in sequence, and install the external hexagonal through bolts 10 exposed on the threaded part of the output shaft flange 6-2 on the right side of the high elastic rubber coupling 6. Install the external hexagonal nut 12 and tighten it manually; then reset the other side of the highly elastic rubber coupling 6 and connect it to the left rigid gear ring 6-1, install the bolts removed previously in situ according to the position marks, and tighten the bolts manually; finally, take out the four tooling support rods installed previously from one side of the gear box flange 9, and then install four external hexagonal through bolts 10 with holes, and similarly install the external hexagonal nut 12 on the other exposed threaded part and tighten it manually.

[0067] Step h: mesh the inertia disc gear ring 8-9 of the inertia disc 8 with the power output gear of the electric turning mechanism, turn the entire marine propulsion diesel engine shaft system, and measure the radial centering circular runout error of the high-elastic rubber coupling 6 every 60 degrees. Specifically, use a dial indicator to measure the radial centering circular runout of the high-elastic rubber coupling 6 to ensure that the radial centering allowable tolerance of the high-elastic rubber coupling 6 is within ±0.5mm.

[0068] Step i: After completing the data measurement required by the above step h, first use a torque wrench to tighten the bolts that fasten the high elastic rubber coupling 6 and the left rigid gear ring 6-1 in sequence according to the required torque, then use a torque wrench to tighten the outer hexagonal nut 12 on the side of the right output shaft flange 6-2 of the high elastic rubber coupling 6 in sequence according to the preload force of 2000N.m, and then install an identical outer hexagonal nut 12 on the outside of the outer hexagonal nut 12, and tighten it with the same torque as above, so as to achieve double nut loosening prevention. On one side of the gearbox flange 9, use an anti-loosening steel wire 11 to pass through the through holes of the two pairs of outer hexagonal through bolts 10 with holes to lock them together to prevent the outer hexagonal through bolts 10 with holes from loosening during operation. At this point, the entire marine propulsion diesel engine and gearbox with inertia disc quick connection device is installed.

[0069] The utility model has a simple structural design, low processing and manufacturing costs, and high on-site installation efficiency. At the same time, it can avoid the gear meshing impact phenomenon that occurs when the gear box is running, reduce the noise generated when the gear box is running, and ultimately improve the stability of the entire shaft system operation of the marine propulsion diesel engine, laying a solid foundation for the reliable and stable operation of the gear box in the later stage.

[0070] It is obvious to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the present invention can be implemented in other specific forms without departing from the spirit or essential features of the present invention. Therefore, the embodiments should be regarded as exemplary and non-restrictive from any point of view, and the scope of the present invention is defined by the appended claims rather than the above description, and it is intended that all changes falling within the meaning and scope of the equivalent elements of the claims are included in the present invention. Any reference numeral in a claim should not be regarded as limiting the claim to which it relates.

[0071] In addition, it should be understood that although the present specification is described according to implementation modes, not every implementation mode contains only one independent technical solution. This description of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other implementation modes that can be understood by those skilled in the art.

Claims

1. A quick connection device with an inertia disc between a marine propulsion diesel engine and a gearbox, characterized in that: It comprises a crankshaft flange (1) of a marine propulsion diesel engine, a rigid flywheel (5), a highly elastic rubber coupling (6), an inertia disc (8), and a gear box flange (9); The marine propulsion diesel engine crankshaft flange (1) is tightly connected to a rigid flywheel (5), the rigid flywheel (5) is tightly connected to a left rigid gear ring (6-1) of a high elastic rubber coupling (6), and the right output shaft flange (6-2) of the high elastic rubber coupling (6) is tightly connected to an inertia disc (8) and a gear box flange (9); the inertia disc (8) is arranged between the high elastic rubber coupling (6) and the gear box flange (9), and the inertia disc (8) is provided with a turning gear ring; The fastening connection between the crankshaft flange (1) of the marine propulsion diesel engine and the rigid flywheel (5), and the fastening connection between the right output shaft flange (6-2) of the high elastic rubber coupling (6) and the inertia disc (8) and the gear box flange (9) are all non-hinged clearance fit between the inner diameter of the through hole and the outer diameter of the non-threaded part of the stud and bolt.

2. The quick connection device with inertia disc between a marine propulsion diesel engine and a gearbox according to claim 1 is characterized in that: The marine propulsion diesel engine crankshaft flange (1) is fastened to a rigid flywheel (5) through a double-headed through-hole stud (2), a slotted nut (3), and a cotter pin (4), wherein the two slotted nuts (3) are respectively mounted on the left and right stud heads of the double-headed through-hole stud (2), and the cotter pin (4) is respectively mounted in the left and right stud head through holes of the double-headed through-hole stud (2); The right output shaft flange (6-2) of the high elastic rubber coupling (6) is fastened to the inertia disc (8) and the gear box flange (9) by means of external hexagonal through-bolts with holes (10), anti-loosening steel wires (11) and external hexagonal nuts (12), wherein the anti-loosening steel wires (11) pass through the through holes of two groups of external hexagonal through-bolts with holes (10) to lock them together, and the external hexagonal nuts (12) are installed in pairs at the threads of the external hexagonal through-bolts with holes (10) in pairs of two groups; The double-headed through-hole studs (2) and slotted nuts (3) of the fasteners for the centering connection between the crankshaft flange (1) of the marine propulsion diesel engine and the rigid flywheel (5) adopt a large torque preload; at the same time, the hexagonal through-hole bolts (10) and hexagonal nuts (12) of the fasteners for the centering connection between the right output shaft flange (6-2) of the high elastic rubber coupling (6), the inertia disc (8) and the gear box flange (9) also adopt a large torque preload.

3. The quick connection device with inertia disc between a marine propulsion diesel engine and a gearbox according to claim 2 is characterized in that: The rigid flywheel (5) is a stepped concave hollow structure, and its material is Q275A\GB / T 700-2006; specifically, it comprises a threaded hole (5-1), a flywheel through hole (5-2), a marking hole "0" (5-3), a center circle through hole (5-4), an inner circle surface of the center circle through hole (5-4-1), a boss (5-5), a boss end surface (5-5-1), a boss outer circle surface (5-5-2), a groove (5-6), a groove end surface (5-6-1), a groove outer circle surface (5-6-2), a flywheel outer circle surface (5-7), a flywheel outer circle end surface (5-8), a flywheel stop groove (5-9), a flywheel stop groove outer circle surface (5-9-1), a flywheel stop groove end surface (5-9-2), and a flywheel outer circle surface hoisting tool mounting hole (5-10); The threaded holes (5-1) are provided with a plurality of holes evenly distributed on the diameter The thread type adopts GB / T193-2003 blind hole; the flywheel through hole (5-2) is provided with a plurality of holes evenly distributed on the diameter The marking hole "0" (5-3) is located on the center line of the rigid flywheel (5) in the vertical direction and is L1 away from the center point. The two ends of the center line of the marking hole "0" (5-3) center line with an angle A1 are marked on the flywheel outer surface (5-7), and the two ends of the center line of the marking hole "0" (5-3) center line with an angle A2 are marked on the flywheel outer surface (5-7). The top dead center mark of each cylinder stroke is used to facilitate the adjustment of the injection advance angle and the rotation phase angle of each cylinder during the installation of the marine propulsion diesel engine when the shaft system is connected and aligned; the center circle through hole (5-4) is a weight removal hole of the rigid flywheel (5), and its diameter is The width value L4 ensures that the rigid flywheel (5) maintains a reasonably set moment of inertia value under the existing volume. The inner circular surface (5-4-1) of the central circular through hole serves as the processing reference A of the entire rigid flywheel (5); the boss end surface (5-5-1) of the boss (5-5) serves as the processing reference B of the entire rigid flywheel (5), and the surface roughness Ra=3.2um. The boss outer circular surface (5-5-2) of the boss (5-5) has a diameter of The width value is L2, the angle between the outer cylindrical surface (5-5-2) of the boss and the outer cylindrical end surface (5-8) of the flywheel is rounded R3 to eliminate concentrated stress and residual stress during processing; the surface roughness Ra of the groove end surface (5-6-1) of the groove (5-6) is 3.2um, and the diameter of the outer cylindrical surface (5-6-2) of the groove (5-6) is The width of the groove (5-6) is L5-L4-L6, and the angle between the groove end surface (5-6-1) and the groove outer cylindrical surface (5-6-2) is rounded R1 to eliminate concentrated stress and processing residual stress; the diameter of the flywheel outer cylindrical surface (5-7) is The width of the flywheel outer circumferential surface (5-7) and the width L2 of the boss outer circumferential surface (5-5-2) constitute the total width L3 of the rigid flywheel (5); the diameter of the flywheel stop groove outer circumferential surface (5-9-1) of the flywheel stop groove (5-9) is The width is L6, and the angle between the outer cylindrical surface (5-9-1) of the flywheel stop groove and the end surface (5-9-2) of the flywheel stop groove is rounded R1 to eliminate concentrated stress and residual stress during processing. At the same time, the end surface of the outer cylindrical surface (5-9-1) of the flywheel stop groove is chamfered C1 to avoid scratching the surface of the part during installation; and a plurality of flywheel outer cylindrical surface hoisting tool installation holes (5-10) are evenly distributed along the circumferential direction on the flywheel outer cylindrical surface (5-7) of the rigid flywheel (5).

4. The quick connection device with inertia disc between a marine propulsion diesel engine and a gearbox according to claim 3 is characterized in that: The marine propulsion diesel engine crankshaft flange (1) and the left rigid gear ring (6-1) of the high elastic rubber coupling (6) are respectively connected to the central circular through hole (5-4) and the flywheel stop groove (5-9) of the rigid flywheel (5), wherein the marine propulsion diesel engine crankshaft flange (1) is in contact and fastened with the boss end face (5-5-1) of the rigid flywheel (5), and the left rigid gear ring (6-1) of the high elastic rubber coupling (6) is in contact and fastened with the flywheel stop groove end face (5-9-2) of the rigid flywheel (5); The verticality of the boss end face (5-5-1) relative to the center circle through hole inner circle face (5-4-1) reference A is 0.04mm and the surface roughness Ra=1.6um, the coaxiality of the flywheel stop groove outer circle face (5-9-1) relative to the center circle through hole inner circle face (5-4-1) reference A is 0.05mm and the verticality of the flywheel stop groove end face (5-9-2) relative to the center circle through hole inner circle face (5-4-1) reference A is 0.04mm, and the flywheel stop The parallelism of the end face of the groove (5-9-2) relative to the datum B of the boss end face (5-5-1) is 0.04 mm, the verticality of the datum B of the boss end face (5-5-1) relative to the datum A of the inner circular surface (5-4-1) of the center circle through hole is 0.04 mm, and the surface processing roughness Ra=3.2 um; the surface roughness Ra of the groove end face (5-6-1) of the groove (5-6) is 3.2 um, and the diameter of the outer circular surface (5-6-2) of the groove (5-6) is The width L5-L4-L6 of the groove (5-6) provides installation space for the double-headed through-hole stud (2), the slotted nut (3) and the cotter pin (4) to be fastened and connected on one side of the rigid flywheel (5); the hole diameter of the flywheel through hole (5-2) of the rigid flywheel (5) is greater than or equal to the outer diameter of the double-headed through-hole stud (2) and forms a small clearance fit.

5. The quick connection device with inertia disc between a marine propulsion diesel engine and a gearbox according to claim 2, characterized in that: The inertia disc (8) is a stepped concave-convex hollow structure, and its material is selected from Q275A\GB / T 700-2006; specifically, it comprises a disc through hole (8-1), a disc hoisting hole (8-2), a central weight-removing through hole (8-3), an inner circle of the central weight-removing through hole (8-3-1), a stop boss (8-4), an outer circle of the stop boss (8-4-1), a disc stop groove (8-5), a disc stop groove end face (8-5-1), an inertia disc step circle surface weight-removing hole (8-6), an inertia disc circle end face (8-7), an inertia disc step circle (8-8), and an inertia disc gear ring (8-9); The disc through holes (8-1) are provided with a plurality of holes evenly distributed on the diameter The disk hoisting holes (8-2) are provided with two and are arranged symmetrically about the central axis, the angle between the disk hoisting holes (8-2) and the vertical center line of the inertia disk (8) is B11, and the two disk hoisting holes (8-2) are distributed in the diameter The center de-weighting through hole (8-3) comprises a center de-weighting through hole inner circle (8-3-1), and the diameter size of the center de-weighting through hole inner circle (8-3-1) is The inner circle of the center weight-removing through hole (8-3-1) serves as the processing reference A of the entire inertia disk (8), and the surface roughness Ra=1.6um; the stop boss (8-4) includes a stop boss outer circle (8-4-1), the length of the stop boss (8-4) is L13, and the outer circle diameter size of the stop boss outer circle (8-4-1) is The disk stop groove (8-5) comprises a disk stop groove end surface (8-5-1), and the diameter of the disk stop groove (8-5) is The depth is L15-L14; a plurality of the inertia disc step circular surface deweighting holes (8-6) are evenly distributed along the outer circumference of the inertia disc step circle (8-8); the distance between the center line of the inertia disc step circular surface deweighting hole (8-6) and the left end surface of the inertia disc step circle (8-8) is L11; and the inertia disc step circular surface deweighting hole (8-6) is arranged together with the central deweighting through hole (8-3) as an auxiliary deweighting hole to ensure that the entire inertia disc (8) maintains a reasonable The inertia moment of inertia is set at a value; the circular end surface (8-7) of the inertia disc is used as the processing reference B of the entire inertia disc (8), and the surface roughness Ra=3.2um; the inertia disc gear ring (8-9) is processed in an integrated manner with the inertia disc (8), and the tooth shape of the inertia disc gear ring (8-9) adopts a standard involute straight tooth, with a tooth number Z=110, a pressure angle a=20°, a module m=10, a pitch circle diameter d=1100mm, and a span of 13 teeth. The length of the common normal line The tooth root fillet radius r′=0.5mm, and the processing accuracy is implemented in accordance with GB / T10095.2-2008-Q9; the rounded corner R4 at the angle between the inertia disc step circle (8-8) and the inertia disc gear ring (8-9) can eliminate the concentrated stress at the tooth root of the inertia disc gear ring (8-9) during operation and the residual stress during processing; the right angle of the end face of the stop boss outer circle (8-4-1) is rounded R5.

6. The quick connection device with inertia disc between a marine propulsion diesel engine and a gearbox according to claim 5, characterized in that: The right output shaft flange (6-2) of the high elastic rubber coupling (6) is centrally connected to the stop boss (8-4) on the left side of the inertia disc (8), and the stop groove (8-5) on the right side of the inertia disc (8) is centrally connected to the gear box flange (9); wherein the groove surface of the right output shaft flange (6-2) of the high elastic rubber coupling (6) is in contact and fastened with the end face of the inertia disc circular end face (8-7) of the stop boss (8-4) on the left side of the inertia disc (8), and the disc stop groove end face (8-5-1) of the disc stop groove (8-5) on the right side of the inertia disc (8) is in contact and fastened with the gear box flange (9); the disc stop groove end face (8-5-1) is relative to the center weight removal through hole. The verticality of the processing datum A of the circle (8-3-1) is 0.02mm, the parallelism of the end face (8-5-1) of the stop groove of the disk relative to the processing datum B of the circular end face (8-7) of the inertia disk is 0.15mm, and the surface roughness Ra of the processing datum A of the inner circle (8-3-1) of the center weight-removing through hole is 1.6um, the surface roughness Ra of the end face (8-5-1) of the stop groove of the disk is 3.2um, and the surface roughness Ra of the processing datum B of the circular end face (8-7) of the inertia disk is 3.2um, and the coaxiality of the outer circle (8-4-1) of the stop boss relative to the processing datum A of the inner circle (8-3-1) of the center weight-removing through hole is 0.04mm; the diameter of the stop boss (8-4) on the left side of the inertia disk (8) is The diameter of the disc stop groove (8-5) on the right side of the inertia disc (8) is smaller than the inner diameter of the output shaft flange (6-2) on the right side of the high elastic rubber coupling (6). The size is larger than the outer diameter of the gear box flange (9), and the above-mentioned matching sizes are all clearance matching; the right output shaft flange (6-2) of the high elastic rubber coupling (6) is fastened with the inertia disc (8) and the gear box flange (9) by multiple groups of circumferentially evenly distributed external hexagonal through-bolts (10), anti-loosening steel wires (11), and external hexagonal nuts (12), and the outer diameter of the external hexagonal through-bolts (10) is smaller than the connection holes of the right output shaft flange (6-2) of the high elastic rubber coupling (6), the inertia disc ( 8) and the inner diameter size of the connecting hole of the disk through hole (8-1) and the gear box flange (9); in addition, two external hexagonal nuts (12) are distributed in each group on one side of the output shaft flange (6-2) of the high elastic rubber coupling (6), and the two external hexagonal nuts (12) are pre-tightened on the threads of the external hexagonal through-bolts (10) with holes in succession, and the anti-loosening steel wire (11) is distributed on the hexagonal position of the external hexagonal through-bolts (10) with holes on one side of the gear box flange (9) and simultaneously locks each group of two external hexagonal through-bolts (10) together.

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