A gear coupling

Abstract

This invention discloses a drum-shaped gear coupling, belonging to the field of coupling transmission technology. The coupling includes an external gear sleeve, a gear end sleeve assembly, and a roller end sleeve assembly. The external gear sleeve has drum-shaped external teeth in the middle and baffles at both ends. The gear end sleeve assembly includes a first internal gear ring that meshes with the drum-shaped external teeth at one end of the external gear sleeve. Its maximum outer diameter does not exceed the outer diameter of the first internal gear ring, and a first axial limiting element is provided to restrict the axial displacement of the external gear sleeve. The roller end sleeve assembly is symmetrically arranged at the other end of the external gear sleeve, along with the gear end sleeve assembly. End caps are provided on the end faces of the internal gear rings at both ends, and a sealing element is provided between the end caps and the outer circle of the external gear sleeve. An oil injection channel is provided on the end caps, with the outlet facing the meshing area of ​​the internal and external teeth. This structure reduces the rotation diameter, achieves small-clearance lubrication at the tooth ends, and reduces maintenance costs.

Description

Technical Field

[0001] This invention relates to the field of coupling transmission technology, and in particular to a drum-shaped gear coupling. Background Technology

[0002] Drum-shaped gear couplings, as rigid-flexible couplings widely used in heavy-duty transmission fields, are extensively applied in the main drive systems of metallurgical steel rolling production lines. For example... Figure 1 As shown, existing drum-shaped gear main couplings generally adopt a split structure consisting of external gear bushings at both ends, an internal gear ring in the middle, an intermediate connecting pipe, and a connecting flange. For example, the coupling structure disclosed in Chinese Patent Application No. CN202520348586.4 has an external gear bushing at both ends connected to the internal gear ring through internal and external teeth, and the middle part is an intermediate connecting pipe, which is connected to the internal gear ring through a flange and bolts.

[0003] However, the above structure has the following drawbacks: 1) To meet the high torque load requirements, the outer diameter of the gear ring must be increased. However, when the outer diameter of the gear ring is increased, the outer diameter of the connecting flange increases simultaneously, causing the overall rotation diameter of the coupling to exceed the reserved space of the equipment frame. If the outer diameter of the gear ring is not increased, the bending strength of the tooth root and the contact strength of the tooth surface are insufficient, which can easily lead to failure problems such as tooth surface peeling and tooth breakage. It is difficult to balance load-bearing capacity and compactness. 2) The split structure has a large number of parts and a large axial length. The additional connecting flanges and intermediate pipes further increase the overall rotation diameter and axial dimension, resulting in more assembly error points and lower transmission accuracy. 3) Due to the limited space of the small gap at the tooth end, if the oil injection hole is opened on the outer circle at the small gap at the tooth end, it will penetrate the root of the inner tooth and weaken the root strength. If the oil hole is not opened at the tooth end, it will be difficult to lubricate the small gap at the tooth end, accelerate tooth surface wear, shorten the maintenance cycle, and increase the downtime and maintenance cost of the rolling line. Summary of the Invention

[0004] 1. The problem to be solved In view of the technical problems existing in the prior art, such as the difficulty in balancing load-bearing capacity and compactness, and insufficient lubrication of couplings, the purpose of this invention is to provide a drum-shaped gear coupling that can at least achieve a miniaturized and compact design of the coupling, and improve transmission stability, lubrication uniformity and sealing reliability.

[0005] 2. Technical Solution To solve the above problems, the technical solution adopted by the present invention is as follows: This invention provides a drum-shaped gear coupling, comprising: An external gear bushing is located in the middle of the coupling. The outer ends of the external gear bushing are provided with a first drum-shaped external tooth and a second drum-shaped external tooth, and the two ends along its central axis are provided with a first end baffle and a second end baffle. A toothed end bushing assembly is disposed at one end of the external toothed bushing. The toothed end bushing assembly includes a first internal toothed ring, which meshes with a first drum-shaped external tooth. The maximum outer diameter of the toothed end bushing assembly does not exceed the outer diameter of the first internal toothed ring. The toothed end bushing assembly is provided with a first axial limiting member inside. The first axial limiting member is configured to limit the axial displacement of the external toothed bushing while allowing the external toothed bushing to deflect relative to the first internal toothed ring. A roller end bushing assembly is disposed at the other end of the external gear bushing. The roller end bushing assembly includes a second internal gear ring, which meshes with the second drum-shaped external gear. The maximum outer diameter of the roller end bushing assembly does not exceed the outer diameter of the second internal gear ring. The roller end bushing assembly is provided with a second axial limiting member inside. The second axial limiting member is configured to limit the axial displacement of the external gear bushing while allowing the external gear bushing to deflect relative to the second internal gear ring. The first internal gear ring has a first end cap on its end face opposite to the external gear sleeve. A first sealing element is provided between the first end cap and the outer circle of the external gear sleeve. The first end cap has a first oil injection channel, and the outlet of the first oil injection channel faces the meshing area between the first internal gear ring and the external gear sleeve. The second internal gear ring has a second end cap on its end face away from the external gear sleeve. A second sealing element is provided between the second end cap and the outer circle of the external gear sleeve. The second end cap has a second oil injection channel, and the outlet of the second oil injection channel faces the meshing area between the second internal gear ring and the external gear sleeve.

[0006] This invention places the external gear bushing in the middle of the coupling, with both ends meshing with the first and second internal gear rings respectively via drum-shaped external teeth, eliminating the need for connecting flanges and intermediate connecting pipes. Since the maximum outer diameter of the bushing assemblies at both ends does not exceed the outer diameter of their respective internal gear rings, the overall maximum rotational diameter of the coupling is determined solely by the outer diameter of the internal gear rings, rather than by the outer diameter of the connecting flange, which is necessarily larger than the inner gear ring's outer diameter in traditional structures. This effectively reduces the rotational diameter while maintaining the same tooth parameters (load capacity). End baffles seal both ends of the external gear bushing, and in conjunction with axial limiting components inside the bushing assemblies, allow the external gear bushing to deflect relative to the internal gear rings while constraining its axial movement, ensuring transmission stability. The oil injection channel outlet on the end cover faces directly towards the meshing area, allowing lubricating oil to reach the small gaps at the tooth ends, solving the problem of inadequate tooth end lubrication caused by limited opening positions in traditional structures.

[0007] In one possible embodiment of the present invention, the first axial limiting member includes a first baffle and a first top block disposed on the first baffle. A ball head is provided on the side of the first top block facing one end face of the external gear sleeve, and the ball head forms a point contact engagement with the end face of the external gear sleeve. The second axial limiting member includes a second baffle and a second top block disposed on the second baffle. A ball head is provided on the side of the second top block facing the other end face of the external gear sleeve, and the ball head forms a point contact engagement with the other end face of the external gear sleeve. The point contact engagement between the ball head and the end face of the external gear sleeve allows the ball head contact point to slide freely on the end face as the deflection angle changes when the external gear sleeve undergoes angular displacement deflection, without interference. This effectively constrains the axial movement of the external gear sleeve while allowing deflection motion.

[0008] In one possible embodiment of the present invention, the end baffle and the external gear sleeve are fixedly connected by welding. The welded connection structure is simple, has high connection strength, and is suitable for working conditions with small axial forces. It can effectively seal the openings at both ends of the external gear sleeve, prevent lubricating oil from flowing into the inner cavity of the external gear sleeve, and concentrate the lubricating oil in the meshing area.

[0009] In one possible embodiment of the present invention, the end baffle and the external gear bushing are connected by bolts, and an O-ring is provided at the connection between the end baffle and the external gear bushing. The bolted end baffle is removable for easy replacement later, and the O-ring forms a reliable seal at the connection, which is suitable for heavy-load conditions with large axial forces and high wear.

[0010] In one possible embodiment of the present invention, the first end cover has a split structure, being divided into two halves along the diameter direction. The two halves of the first end cover are bolted together to form a complete ring and fixed to the end face of the first internal gear ring. A sealing groove is provided inside the first end cover, and an O-ring is provided within the sealing groove. Similarly, the second end cover has a split structure, being divided into two halves along the diameter direction. The two halves of the second end cover are bolted together to form a complete ring and fixed to the end face of the second internal gear ring. A sealing groove is provided inside the second end cover, and an O-ring is provided within the sealing groove. The split end cover facilitates installation and disassembly with the external gear sleeve already inserted, eliminating the need for complete disassembly of the coupling. A reliable radial seal is formed between the O-ring and the outer circumference of the external gear sleeve, effectively preventing lubricant leakage.

[0011] In one possible embodiment of the present invention, the first oil injection channel is formed on the end face of the first end cap, and the axial projection position of the first oil injection channel is offset from the position of the split seam of the first end cap; the second oil injection channel is formed on the end face of the second end cap, and the axial projection position of the second oil injection channel is offset from the position of the split seam of the second end cap. By forming the oil injection channels on the end face of the end cap rather than on the outer circumference of the tooth tip, the problem of the opening penetrating the root of the internal tooth and weakening the tooth root strength is avoided; the axial projection position of the oil injection channel is offset from the split seam, preventing lubricating oil leakage from the split seam, ensuring the sealing reliability of the oil injection channels, and each baffle can reduce the amount of lubricating oil used.

[0012] In one possible embodiment of the present invention, the end face of the first internal gear ring facing the first end cap has a sealing groove, and an O-ring is provided in the sealing groove. The O-ring contacts the end face of the first end cap to form an end face seal. The end face of the second internal gear ring facing the second end cap has a sealing groove, and an O-ring is provided in the sealing groove. The O-ring contacts the end face of the second end cap to form an end face seal. The O-ring in the sealing groove of the internal gear ring contacts the end face of the end cap, forming a static end face seal at the mating surface of the internal gear ring and the end cap. Together with the radial seal inside the end cap, this forms a double sealing system, further reducing lubricating oil leakage from the mating surface.

[0013] In one possible embodiment of the present invention, the first internal gear ring is provided with a main oil injection hole, which is opened at the connection end between the first internal gear ring and the bushing of the gear end bushing assembly. The main oil injection hole connects the meshing area of ​​the first internal gear ring and the external gear bushing, and the main oil injection hole is symmetrically arranged circumferentially along the first internal gear ring. Similarly, the second internal gear ring is provided with a main oil injection hole, which is opened at the connection end between the second internal gear ring and the bushing of the roller end bushing assembly. The main oil injection hole connects the meshing area of ​​the second internal gear ring and the external gear bushing, and the main oil injection hole is symmetrically arranged circumferentially along the second internal gear ring. The main oil injection hole, located at the connection end between the internal gear ring and the bushing, introduces lubricating oil into the meshing area from the bushing connection end direction, forming a bidirectional lubrication supply with the oil injection channel on the end cap end face. The circumferentially symmetrical arrangement ensures uniform distribution of lubricating oil in the meshing area.

[0014] In one possible embodiment of the present invention, the first baffle is bolted to the bushing of the toothed end bushing assembly, and an O-ring is provided at the connection between the first baffle and the bushing of the toothed end bushing assembly; the second baffle is bolted to the bushing of the roller end bushing assembly, and an O-ring is provided at the connection between the second baffle and the bushing of the roller end bushing assembly.

[0015] 3. Beneficial effects Compared with the prior art, the beneficial effects of the present invention are as follows: (1) By placing the external gear shaft sleeve in the middle of the coupling and setting internal gear rings at both ends to mesh with the external gear shaft sleeve, and eliminating the connecting flange and intermediate pipe, the maximum rotation diameter of the coupling is determined only by the outer diameter of the internal gear ring. This eliminates the structural root cause of the rotation diameter exceeding the limit in the traditional structure, where the outer diameter of the connecting flange is necessarily larger than the outer diameter of the internal gear ring. Under the premise that the tooth bearing parameters remain unchanged, the rotation diameter of the coupling is effectively reduced, which solves the technical contradiction that the bearing capacity and compactness of the traditional main coupling cannot be balanced. This allows the coupling to be adapted to the installation space of a compact transmission system. (2) The present invention eliminates the intermediate pipe and connecting flange, and replaces the traditional structure of two-end external gear bushings plus intermediate pipe with a single external gear bushing. This effectively reduces the number of parts, shortens the overall axial length of the coupling, reduces assembly error points, improves transmission accuracy, and at the same time reduces the manufacturing cost and installation difficulty of the coupling. The axial limiting parts set inside the bushing assembly at both ends allow the external gear bushing to deflect while constraining the axial movement, ensuring the stability of transmission under the premise of compact structure. (3) The end cap of the present invention has an oil injection channel on the end face, so that the outlet of the oil injection channel is directly facing the meshing area of ​​the inner and outer teeth. The lubricating oil can reach the small gap at the tooth end along the axial direction, which solves the problem of insufficient lubrication caused by the opening of the outer circle of the tooth end in the traditional structure, which will penetrate the root of the inner tooth. Sufficient lubrication at the small gap at the tooth end is achieved without weakening the strength of the root of the inner tooth. The dual sealing system formed by the O-ring of the sealing groove of the inner tooth ring end face and the radial seal of the split end cap effectively reduces the leakage of lubricating oil, extends the lubrication cycle, and reduces the downtime and maintenance cost of the rolling line. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0017] Figure 1 A schematic diagram of the structure of a drum-shaped gear coupling in the prior art; Figure 2 This is a schematic diagram of the overall structure of the drum-shaped gear coupling provided in Embodiment 1 of the present invention; Figure 3 This is a cross-sectional view of the drum-shaped gear coupling provided in Embodiment 1 of the present invention; Figure 4 This is a schematic diagram of the external gear bushing structure provided in Embodiment 1 of the present invention; Figure 5 for Figure 3 Enlarged view of part A in the image; Figure 6 for Figure 3 Enlarged view of part B in the image; Figure 7 This is a cross-sectional view of the welded split-type drum gear coupling structure provided in Embodiment 2 of the present invention; Figure 8 This is a cross-sectional view of the double-stud detachable drum gear coupling provided in Embodiment 3 of the present invention; Figure 9 for Figure 8 Enlarged view of section C in the image.

[0018] Explanation of reference numerals in the attached figures: 100. External gear bushing; 110. First drum-shaped external gear; 120. Second drum-shaped external gear; 130. First end baffle; 140. Second end baffle; 200. Gear end bushing assembly; 210. First internal gear ring; 220. First axial limiting member; 221. First baffle; 222. First top block; 223. First ball head; 230. First end cover; 231. Sealing groove; 232. O-ring seal; 233. Splitting seam; 240. First seal; 250. First oil injection channel; 260. First main oil injection hole; 300. Roller end bushing assembly; 310. Second internal gear ring; 320. Second axial limiting component; 321. Second baffle; 322. Second top block; 323. Second ball head; 330. Second end cap; 340. Second seal; 350. Second oil injection channel; 360. Second main oil injection hole. Detailed Implementation

[0019] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of the present invention. However, the present invention can be practiced in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0020] Example 1 like Figures 2 to 6 As shown, this embodiment provides a compact drum-shaped gear coupling, which is a preferred high-strength implementation structure of the present invention and is suitable for heavy-duty transmission conditions with high load, high speed, and continuous operation.

[0021] like Figure 2 and Figure 3 As shown, the overall structure of the aforementioned drum-shaped gear coupling includes an external gear bushing 100 assembly arranged in the center, a tooth end bushing assembly 200 and a roller end bushing assembly 300 symmetrically assembled at both ends of the external gear bushing 100 assembly, with the external gear bushing 100 assembly serving as the transmission base.

[0022] In this embodiment, as Figure 4 As shown, both ends of the external gear bushing 100 assembly are precision-machined with drum-shaped external teeth. The tooth surfaces are treated with high-frequency quenching, which effectively improves hardness and wear resistance, and can effectively resist long-term meshing wear and impact loads. The two end faces of the external gear bushing 100 assembly are welded to the annular first end baffle 130 and the second end baffle 140 through a full welding process. The weld is full and free of pores. After welding, the entire assembly is ground and leveled to ensure the flatness of the end faces. This achieves both rigid fixation of the first end baffle 130, the second end baffle 140 and the external gear bushing 100 assembly, and avoids the problem of gap loosening. The structure has good integrity and stability and can withstand high-frequency impact torque.

[0023] It should be noted that in this embodiment, the toothed end bushing assembly 200 and the roller end bushing assembly 300 are symmetrically arranged at both ends of the external toothed bushing 100 assembly. The connecting flange, intermediate pipe and connecting bolt group required by traditional couplings are eliminated between the two sets of bushing assemblies, and redundant transition structures are discarded, thereby reducing the axial and radial dimensions of the coupling from the source. At the same time, the overall outer diameter of the toothed end bushing assembly 200 is controlled by the outer diameter of the first internal gear ring 210, and the overall outer diameter of the roller end bushing assembly 300 is controlled by the outer diameter of the second internal gear ring 310. There are no protruding mounting structures, limiting structures and connecting structures, and the overall radial dimension is minimized, achieving an extremely compact structural design.

[0024] The internal teeth of the first internal gear ring 210 and the second internal gear ring 310 mentioned above mesh with the drum-shaped external teeth at both ends of the external gear bushing 100 assembly. The drum-shaped tooth structure can adapt to the angular offset, radial offset and axial movement between the two transmission shafts, and has a good deviation compensation capability, effectively offsetting the shaft offset caused by equipment installation errors and operating vibrations.

[0025] In addition, such as Figure 6 As shown, a first axial limiting member 220 is fixedly assembled inside the toothed end bushing assembly 200, and a second axial limiting member 320 is fixedly assembled inside the roller end bushing assembly 300. The two sets of axial limiting members are also arranged symmetrically. The first axial limiting member 220 is made of wear-resistant alloy steel and consists of a first baffle 221 and an integrated first top block 222. The end of the first top block 222 is precision machined into an arc-shaped spherical structure to form a first ball head 223. The first ball head 223 and the end face of the external toothed bushing 100 assembly are in a point contact fit mode. The second axial limiting member 320 is made of wear-resistant alloy steel and consists of a second baffle 321 and an integrated second top block 322. The end of the second top block 322 is precision machined into an arc-shaped spherical structure to form a second ball head 323. The second ball head 323 and the end face of the external toothed bushing 100 assembly are in a point contact fit mode.

[0026] Compared to traditional planar rigid limiting and stepped limiting structures, the above-described point contact limiting method has no jamming constraint. When the external gear bushing 100 assembly undergoes a small angular deflection and radial runout with the transmission shaft, the ball head can adaptively slide against the end face without causing hard interference to the shaft deflection. At the same time, it can limit the axial displacement of the external gear bushing 100 assembly, effectively avoiding the problems of misalignment of internal and external gear meshing and end face impact wear, and effectively improving the transmission stability under high-speed operation conditions.

[0027] Furthermore, such as Figure 3 and Figure 5 As shown, the outer end faces of the first internal gear ring 210 and the second internal gear ring 310 are respectively detachably fitted with the first end cover 230 and the second end cover 330. Both sets of end covers adopt a split structure with axial splitting. During disassembly and assembly, it is not necessary to disassemble the shafts of the transmission equipment at both ends. They can be directly split in half and removed, greatly reducing the difficulty of equipment maintenance, seal replacement, and lubrication. The two halves of the end cover are spliced ​​and locked into a complete ring structure by evenly arranged fastening bolts, which fit and fix to the corresponding end face of the internal gear ring.

[0028] The first end cap 230 and the second end cap 330 have the same structure. The end face area of ​​the first end cap 230 is provided with a sealing groove 231. The sealing groove 231 closes synchronously with the end cap splicing. A suitable O-ring seal 232 is installed in the groove. After fitting and assembling with the first internal gear ring 210, an end face sealing structure is formed. At the same time, the annular area of ​​the inner hole of the first end cap 230 is also provided with a sealing groove. The first sealing element 240 (split O-ring seal) is installed and assembled with the outer circle of the intermediate shoulder of the external gear bushing 100 to form a radial sealing structure. A dual sealing system of radial sealing and end face sealing is constructed, which can effectively prevent external dust, water vapor and oil from entering the meshing area, while avoiding leakage of internal lubricating grease.

[0029] Similarly, a sealing groove is provided on the end face area of ​​the second end cover 330. The sealing groove closes synchronously with the splicing of the end cover. A suitable O-ring 232 is installed in the groove. After fitting and assembling with the second internal gear ring 310, an end face sealing structure is formed. At the same time, a sealing groove is also provided in the annular area of ​​the inner hole of the second end cover 330. A second sealing element 340 (split O-ring) is installed and assembled with the outer circle of the intermediate shoulder of the external gear bushing 100 to form a radial sealing structure. A dual sealing system of radial sealing and end face sealing is constructed, which can effectively prevent external dust, water vapor and oil from entering the meshing area, while avoiding leakage of internal lubricating grease.

[0030] like Figure 3As shown, the end faces of the first end cap 230 and the second end cap 330 are vertically provided with through-type oil injection channels, namely the first oil injection channel 250 and the second oil injection channel 350. The axial projection positions of all oil injection channels are staggered with the split seam 233 of the end cap to avoid the sealing splice gap and prevent grease from leaking or leaking air from the gap during oil injection.

[0031] The outlets of the first oil injection channel 250 and the second oil injection channel 350 are aligned with the meshing contact surfaces of the internal and external teeth, allowing lubricating grease to be directly introduced into the small gaps at the tooth ends. Simultaneously, two sets of first main oil injection holes 260 and second main oil injection holes 360 are symmetrically opened circumferentially at the connection ends of the first internal gear ring 210, the second internal gear ring 310, and the bushing. These first and second main oil injection holes 260 and 360 obliquely extend to the meshing area of ​​the tooth surface, forming a multi-point lubrication structure with the end cover oil injection channels. During routine maintenance, oil can be replenished through the end cover oil injection channels. For long-term operation, full-area oil replenishment can be performed through the main oil injection holes of the internal gear rings, ensuring uniform adhesion of lubricating grease across the entire circumference of the tooth surface, forming a stable lubricating oil film, effectively reducing tooth surface meshing friction loss and slowing down wear and aging.

[0032] Example 2 like Figure 7 As shown in this embodiment, the bushing base of the toothed end bushing assembly 200 and the roller end bushing assembly 300, along with the corresponding internal gear ring, are both separately machined and integrally welded and fixed structures. The welding adopts submerged arc automatic welding process, and stress-relief annealing treatment is performed after welding to eliminate residual welding stress and prevent deformation and loosening after long-term operation. After welding, the bushing and the internal gear ring are integrally precision machined to ensure coaxiality and roundness accuracy, resulting in extremely high transmission rigidity without relative movement or offset. It can stably adapt to heavy industrial working conditions such as metallurgical rolling mills, mining crushers, and large fans that require high torque, high speed, and continuous 24-hour operation.

[0033] The coupling in this embodiment is easy to manufacture and process, and easy to return to the factory for repair. During production, this split-type processing is easier to achieve compared to the one-piece machining solution. During maintenance, since the gear part is the part with the most wear, the internal gear ring can be directly machined off, replaced with a new internal gear ring, and then re-welded.

[0034] Example 3 like Figure 8 and Figure 9As shown, this embodiment is a preferred detachable and maintainable structure. The overall main structure, limiting structure, lubrication structure, and sealing structure are consistent with Embodiment 1. The core difference lies in the connection and fixing method of the components, adapting to general transmission conditions requiring regular loads and periodic maintenance. In this embodiment, the end faces of the end baffle and the external gear bushing 100 assembly are detachably connected by high-precision bolts. An annular sealing groove is opened between the connecting end faces of the baffle and the bushing, and an O-ring is installed to ensure a tight connection while achieving end face sealing, preventing dust ingress and grease leakage. Compared to the welded structure, the bolt connection allows for quick disassembly of the end baffle, facilitating replacement after wear (especially in cases of significant axial movement).

[0035] Meanwhile, the bushings in the gear end bushing assembly 200 and the roller end bushing assembly 300 adopt a split double-ended stud locking connection method with the corresponding internal gear ring, abandoning the welded integrated structure. Multiple sets of double-ended studs are evenly arranged circumferentially to ensure uniform connection force and high coaxiality accuracy. A flat sealing gasket and an O-ring are installed between the mating end faces of the bushing and the internal gear ring to seal the connection gaps, ensure the sealing of the connection position, and prevent oil leakage and dust ingress. When a single component is worn or aged, the corresponding component can be disassembled and replaced separately without replacing the entire coupling, effectively reducing equipment maintenance costs and minimizing spare parts waste. At the same time, compared with the integrated processing solution, this embodiment is also easier to manufacture. The overall assembly of this embodiment has high precision and is easy to maintain, making it suitable for industrial transmission scenarios with conventional loads and intermittent operation, such as conveying equipment, chemical pumps, and general-purpose reducers.

[0036] The drum-shaped gear couplings described in Examples 1-3 above can be widely used in various industrial transmission equipment that require maintenance-free long-term operation in confined installation spaces, dusty and humid conditions, alternating high and low speed transmissions, and in typical application scenarios. The specific application effects are illustrated below: (1) Compact and confined space equipment scenarios (precision conveying equipment, small chemical units): Traditional drum-shaped gear couplings, due to their intermediate connecting pipes and connecting flange structures, have large axial lengths and numerous radially protruding structures, making them unsuitable for equipment with compact frames and extremely limited installation space. This invention eliminates all intermediate transitional connection structures, reducing the overall volume by more than 30%, and has no protruding outer diameter structures, allowing direct adaptation to confined installation positions. After application, the equipment assembly is close-fitting and structurally regular, with no spatial interference issues. At the same time, thanks to the staggered oil injection structure and multiple sealing design, it can resist workshop dust and slight moisture erosion, ensuring no oil leakage or jamming during long-term operation, effectively improving the stability of equipment operation.

[0037] (2) Heavy-duty continuous operation conditions (mining crushers, metallurgical rolling mills, large induced draft fans): These types of equipment have large load torque, frequent vibration, and operate continuously for 24 hours. Traditional rigid limit couplings are prone to problems such as tooth surface wear, axial movement, and transmission jamming. The high-rigidity welded structure of Embodiment 2 of this invention has high overall torsional strength and no structural loosening. Combined with the ball head point contact axial limit structure, it can adapt to the shaft angle offset and radial runout caused by the vibration of the equipment operation, effectively avoiding stress concentration and excessive wear of local tooth surfaces. At the same time, the multi-point lubrication structure can ensure the continuous stability of the tooth surface lubricating oil film under high speed and heavy load. Compared with traditional couplings, the continuous operating life of the equipment is increased by more than 40%, effectively reducing the frequency of downtime maintenance and ensuring continuous operation of the production line.

[0038] (3) Conventional general operation and maintenance conditions (industrial water pumps, reducer drives, material conveyor units): The wear cycle of parts in this type of equipment is short and regular inspection and maintenance are required. Traditional welded integrated couplings are cumbersome to repair and disassemble, and the replacement cost is high. The detachable structure of Embodiment 3 of this invention can quickly disassemble the end cover, bushing, internal gear ring and other parts, and replace worn parts individually without disassembling the entire transmission unit. The operation and maintenance efficiency is improved by more than 60%, and the equipment operation and maintenance cost is effectively reduced. The multi-seal structure can effectively resist the humid and dusty environment of the outdoors and workshop, and eliminate the problems of seal failure, oil leakage and dust ingress. It is suitable for most general industrial transmission scenarios and has strong versatility and practicality.

[0039] It should be noted that those skilled in the art can make various modifications and improvements without departing from the inventive concept, and these all fall within the scope of protection of this invention. Therefore, the scope of protection of this patent should be determined by the appended claims.

Claims

1. A drum-shaped gear coupling, characterized in that, include: An external gear sleeve (100) is located in the middle of the coupling. The outer ends of the external gear sleeve (100) are provided with a first drum-shaped external tooth (110) and a second drum-shaped external tooth (120). The two ends along its central axis are provided with a first end baffle (130) and a second end baffle (140). A toothed end bushing assembly (200) is disposed at one end of the external toothed bushing (100). The toothed end bushing assembly (200) includes a first internal toothed ring (210), which meshes with the first drum-shaped external tooth (110). The maximum outer diameter of the toothed end bushing assembly (200) does not exceed the outer diameter of the first internal toothed ring (210). The toothed end bushing assembly (200) is provided with a first axial limiting member (220) inside. The first axial limiting member (220) is configured to limit the axial displacement of the external toothed bushing (100) while allowing the external toothed bushing (100) to deflect relative to the first internal toothed ring (210). A roller end bushing assembly (300) is disposed at the other end of the external gear bushing (100). The roller end bushing assembly (300) includes a second internal gear ring (310), which meshes with the second drum-shaped external gear (120). The maximum outer diameter of the roller end bushing assembly (300) does not exceed the outer diameter of the second internal gear ring (310). The roller end bushing assembly (300) is provided with a second axial limiting member (320) inside. The second axial limiting member (320) is configured to limit the axial displacement of the external gear bushing (100) while allowing the external gear bushing (100) to deflect relative to the second internal gear ring (310). The first internal gear ring (210) has a first end cap (230) on its end face away from the external gear bushing (100). A first seal (240) is provided between the first end cap (230) and the outer circle of the external gear bushing (100). A first oil injection channel (250) is provided on the first end cap (230). The outlet of the first oil injection channel (250) is directed toward the meshing area of ​​the first internal gear ring (210) and the external gear bushing (100). The second internal gear ring (310) has a second end cap (330) on its end face away from the external gear bushing (100). A second seal (340) is provided between the second end cap (330) and the outer circle of the external gear bushing (100). A second oil injection channel (350) is provided on the second end cap (330). The outlet of the second oil injection channel (350) is directed toward the meshing area of ​​the second internal gear ring (310) and the external gear bushing (100).

2. The drum-shaped gear coupling according to claim 1, characterized in that, The first axial limiting member (220) includes a first baffle (221) and a first top block (222) disposed on the first baffle (221). The first top block (222) has a first ball head (223) on the side facing the first end baffle (130). The first ball head (223) and the first end baffle (130) form a point contact engagement. The second axial limiting member (320) includes a second baffle (321) and a second top block (322) disposed on the second baffle (321). The second top block (322) has a second ball head (323) on the side facing the second end baffle (140). The second ball head (323) and the second end baffle (140) form a point contact engagement.

3. The drum-shaped gear coupling according to claim 1, characterized in that, The first end baffle (130), the second end baffle (140), and the external gear bushing (100) are fixedly connected by welding.

4. The drum-shaped gear coupling according to claim 1, characterized in that, The first end cap (230) is a split structure. The first end cap (230) is split into two halves along the diameter direction. The two halves of the first end cap (230) are connected by bolts to form a complete ring and then fixed to the end face of the first internal gear ring (210). The first end cap (230) is provided with a sealing groove (231) and an O-ring (232) is provided in the sealing groove (231). The second end cap (330) is a split structure. The second end cap (330) is split into two halves along the diameter direction. The two halves of the second end cap (330) are connected by bolts to form a complete ring and then fixed to the end face of the second internal gear ring (310). The second end cap (330) is provided with a sealing groove and an O-ring is provided in the sealing groove.

5. The drum-shaped gear coupling according to any one of claims 1-4, characterized in that, The first end cap (230) is provided with a first oil injection channel (250), the outlet of the first oil injection channel (250) is directed toward the meshing area of ​​the first internal gear ring (210) and the external gear bushing (100); and the second end cap (330) is provided with a second oil injection channel (350), the outlet of the second oil injection channel (350) is directed toward the meshing area of ​​the second internal gear ring (310) and the external gear bushing (100).

6. The drum-shaped gear coupling according to claim 5, characterized in that, The first oil injection channel (250) is opened on the end face of the first end cap (230), and the axial projection position of the first oil injection channel (250) is offset from the position of the split seam (233) of the first end cap (230); the second oil injection channel (350) is opened on the end face of the second end cap (330), and the axial projection position of the second oil injection channel (350) is offset from the position of the split seam of the second end cap (330).

7. The drum-shaped gear coupling according to claim 1, characterized in that, A first main oil injection hole (260) is provided at the connection between the first internal gear ring (210) and the bushing of the gear end bushing assembly (200). The first main oil injection hole (260) connects the meshing area of ​​the first internal gear ring (210) and the external gear bushing (100). The first main oil injection hole (260) is symmetrically arranged around the circumference of the first internal gear ring (210). A second main oil injection hole (360) is provided at the connection between the second internal gear ring (310) and the bushing of the roller end bushing assembly (300). The second main oil injection hole (360) connects the meshing area of ​​the second internal gear ring (310) and the external gear bushing (100). The second main oil injection hole (360) is symmetrically arranged around the circumference of the second internal gear ring (310).

8. The drum-shaped gear coupling according to claim 1, characterized in that, The first end baffle (130), the second end baffle (140) and the external gear bushing (100) are connected by bolts, and an O-ring is provided at the connection between the first end baffle (130), the second end baffle (140) and the external gear bushing (100).

9. The drum-shaped gear coupling according to claim 8, characterized in that, The first baffle (221) is bolted to the bushing of the toothed end bushing assembly (200), and an O-ring is provided at the connection between the first baffle (221) and the bushing of the toothed end bushing assembly (200); the second baffle (321) is bolted to the bushing of the roller end bushing assembly (300), and an O-ring is provided at the connection between the second baffle (321) and the bushing of the roller end bushing assembly (300).

Images