Monorail crane driving speed reducer
By using back-to-back tapered roller bearings and planetary gear shaft bearings in the monorail reducer, combined with a centrifugal oil film self-lubricating system and multiple seals, the problems of insufficient load-bearing capacity and lubrication failure of monorails under high load and high speed are solved, achieving stable lubrication and efficient composite load bearing.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- 上海合纵重工机械有限公司
- Filing Date
- 2025-06-20
- Publication Date
- 2026-05-05
AI Technical Summary
Existing monorail reducers have insufficient load-bearing capacity, high risk of lubrication failure, and poor sealing reliability under high load, high speed and complex stress environment, making it difficult to effectively withstand radial and axial combined loads.
It adopts back-to-back tapered roller bearings and planetary gear shaft bearings, combined with a centrifugal oil film self-lubricating system and multiple seals to form independent lubrication chambers, which enhances the bearing's load-bearing capacity and ensures stable lubrication.
Ensuring stable lubrication under high temperature and high speed improves the reducer's composite load-bearing capacity, reduces maintenance costs, and adapts to extreme working conditions of monorail cranes.
Smart Images
Figure CN224201085U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of speed reducer technology, specifically a single-rail crane drive speed reducer. Background Technology
[0002] The background technology of this design is based on the special working conditions of monorail cranes, proposing an optimized solution for their high load, high speed, and complex stress environment. The monorail crane system is driven by a permanent magnet servo motor. Although increasing the rated speed of the motor can enhance the driving power, the matching reducer needs to be adapted to high-speed input, usually exceeding 3000 rpm. This places stringent requirements on gear meshing stability, bearing heat dissipation, and lubrication systems. At the same time, the polyurethane rollers installed at the end of the output shaft run tightly against the guide rail under the pulling force of the hydraulic cylinder, bearing radial loads of up to several tons. Under slope conditions, the inertial impact of the suspended heavy load will cause the output bearing to be subjected to alternating axial forces. Traditional reducers are prone to a sharp reduction in life due to bearing failure or gear pitting.
[0003] Existing monorail reducers mostly use parallel shaft gears or ordinary planetary gear structures, which have the following drawbacks:
[0004] Insufficient load-bearing capacity: Ordinary deep groove ball bearings or single tapered roller bearings are unable to balance high radial and axial combined loads, which can easily lead to bearing fatigue spalling.
[0005] Lubrication failure risk: Insufficient splashing of lubricating oil during high-speed operation can easily lead to dry friction in the contact area between gears and bearings, exacerbating wear.
[0006] Poor sealing reliability: Traditional labyrinth seals or single lip seals are prone to leakage under frequent impacts, resulting in lubricant loss and intrusion of external contaminants.
[0007] Therefore, there is an urgent need to design a monorail drive reducer to form a relatively independent lubrication chamber to enhance the lubrication effect and strengthen the reducer's ability to withstand radial and axial loads. Utility Model Content
[0008] The purpose of this invention is to overcome the shortcomings of the prior art and provide a monorail drive reducer to form a relatively independent lubrication chamber to enhance the lubrication effect and strengthen the reducer's ability to withstand radial and axial loads.
[0009] To achieve the above objectives, a monorail drive reducer is designed, comprising a housing, a high-speed input shaft, a low-speed input shaft, a high-speed planetary carrier, and a low-speed planetary carrier coaxially arranged within the housing, and several high-speed planetary gears and several low-speed planetary gears respectively mounted on the high-speed planetary gear shaft of the high-speed planetary carrier and the low-speed planetary gear shaft of the low-speed planetary carrier. One end of the low-speed input shaft is connected to the high-speed planetary carrier, and the other end is provided with a low-speed sun gear meshing with the low-speed planetary gears. One end of the high-speed input shaft is provided with a high-speed sun gear meshing with the high-speed planetary gears. The high-speed planetary gears and the high-speed planetary gear shafts are connected by cylindrical roller bearings, and the low-speed planetary gears and the low-speed planetary gear shafts are connected by needle roller bearings. The inner wall of the housing is located within the high-speed planetary carrier. A first protrusion is provided in the gap between the carrier and the low-speed planetary carrier. The low-speed planetary carrier has a first extension on the side facing the high-speed planetary carrier. A first step structure is provided on the outer side of the end of the first extension. A second step structure is provided on the end of the first protrusion facing the low-speed planetary carrier. The inner and outer rings of the full-roll bearing are respectively set on the first step structure of the first extension and the second step structure of the first protrusion. The output shaft is connected to the end of the low-speed planetary carrier away from the high-speed planetary carrier. A connecting flange is provided at the end of the housing near the output shaft. The connecting flange has a second extension on the side near the housing. The outer diameter of the second extension is the same as the inner diameter of the end of the housing. The second extension of the connecting flange is engaged in the end of the housing.
[0010] Preferably, the present invention further includes: a first tapered roller bearing and a second tapered roller bearing coaxially arranged between the output shaft and the housing, the first tapered roller bearing being disposed at the end away from the low-speed planetary carrier, and the second tapered roller bearing being disposed at the end close to the low-speed planetary carrier, the first tapered roller bearing and the second tapered roller bearing being installed back to back.
[0011] Preferably, the present invention further includes: a second protrusion structure is provided on the inner wall of the housing between the first tapered roller bearing and the second tapered roller bearing, and the outer rings of the first tapered roller bearing and the second tapered roller bearing are respectively disposed on both sides of the second protrusion structure.
[0012] Preferably, the present invention further includes: a first sealing ring provided between the housing and the output shaft, and between the first tapered roller bearing and the second tapered roller bearing, forming a first sealed cavity inside the housing that is isolated from the first tapered roller bearing; a second sealing ring provided between the second extension of the connecting flange and the inner wall of the housing, forming a second sealed cavity inside the housing that includes only the output shaft and the first tapered roller bearing; an oil filler and a pressure vent cap respectively provided on the housing corresponding to the first tapered roller bearing, a vent cap provided on the housing corresponding to the second tapered roller bearing, and an oil window provided on the housing corresponding to the low-speed planetary carrier.
[0013] Preferably, the present invention further includes: a third step structure on the inner wall of the connecting flange at the end away from the low-speed planetary carrier, and a fourth step structure on the inner wall at the end near the low-speed planetary carrier; a fifth step structure on the output shaft at the end away from the low-speed planetary carrier, the third step structure and the fifth step structure having the same height, a pressure plate being disposed in the third step structure and the fifth step structure, the pressure plate being connected to the output shaft by screws; one end of the adjusting bushing being disposed in the fourth step structure, and the other end being disposed at the top of the inner ring of the first tapered roller bearing near the end of the connecting flange.
[0014] Preferably, the present invention further includes: a self-aligning ball bearing is used to connect the high-speed input shaft and the housing, and a high-pressure sealing ring is provided between the high-speed input shaft and the housing.
[0015] Preferably, the present invention further includes a blue paper baffle between the high-speed input shaft and the housing.
[0016] Compared with the prior art, the advantages of this utility model are:
[0017] It adopts back-to-back tapered roller bearings and planetary gear shaft bearings to improve the composite load-bearing capacity. Combined with a centrifugal oil film self-lubricating system and multiple seals, it ensures stable lubrication at high temperature and high speed (≥3000 rpm). The stepped structure and adjusting bushing simplify assembly, and the split sealing cavity reduces maintenance costs, making it suitable for extreme working conditions of monorail cranes. Attached Figure Description
[0018] Figure 1 This is a sectional view of the drive reducer for a monorail crane;
[0019] In the diagram: 1 Adjusting sleeve, 2 First tapered roller bearing, 3 Oil nozzle, 4 Breather cap, 5 Second tapered roller bearing, 6 Oil window, 7 Needle roller bearing, 8 Full roll bearing, 9 High-speed planetary carrier, 10 Cylindrical roller bearing, 11 Barley paper baffle, 12 Magnetic plug, 13 High-pressure seal ring, 14 Self-aligning ball bearing, 15 High-speed input shaft, 16 Low-speed sun gear, 17 Low-speed planetary carrier, 18 Output shaft screw, 19 Output shaft, 20 First seal ring, 21 Pressure vent cap, 22 Second seal ring, 23 Screw 24 Connecting flange, 25 Pressure plate, 26 First protruding structure, 27 Second protruding structure, 28 First step structure, 29 Second step structure, 30 Third step structure, 31 Fourth step structure, 32 Fifth step structure, 33 High-speed planetary gear shaft, 34 Low-speed planetary gear shaft, 35 Low-speed input shaft, 36 High-speed sun gear, 37 Second extension, 38 First sealing cavity, 39 Second sealing cavity, 40 High-speed planetary gear, 41 Low-speed planetary gear, 42 Housing, 43 First extension. Detailed Implementation
[0020] To make the purpose, principle and structure of this utility model clearer, the following description is provided in conjunction with the accompanying drawings and specific embodiments.
[0021] To meet the high load-bearing capacity, high speed, and self-lubricating requirements of the monorail drive reducer, the following is combined with the appendix. Figure 1 The specific structure of this design is described in detail.
[0022] The main structure of the reducer includes:
[0023] The housing 42 has a high-speed input shaft 15 and a low-speed input shaft 35 coaxially arranged in its inner cavity. The high-speed input shaft 15 is located inside the inner cavity of the housing 42, and one end of the low-speed input shaft 35 is located inside the housing 42, while the other end extends out of the housing 42.
[0024] It also includes a two-stage planetary transmission system, comprising a high-speed stage and a low-speed stage, housed within the housing 42.
[0025] The high-speed stage includes: a high-speed sun gear 36 fixedly mounted on a high-speed input shaft 15; and several high-speed planetary gears 40 symmetrically arranged around the high-speed sun gear 36 with the high-speed input shaft 15 as the center of symmetry, forming a planetary gear system structure. The outer rings of the high-speed sun gear 36 and the high-speed planetary gears 40 mesh with each other. A high-speed planetary carrier 9 is coaxially mounted with the high-speed input shaft 15 and avoids contact with it. Several high-speed planetary gear shafts 33 are mounted on the high-speed planetary carrier 9, and the high-speed planetary gears 40 are fixedly mounted on the high-speed planetary gear shafts 33. The high-speed planetary gears 40 are fitted with the high-speed planetary gear shafts 33 through cylindrical roller bearings 10. The inner ring of the cylindrical roller bearing 10 is fitted on the high-speed planetary gear shaft 33, and the outer ring is interference-fitted with the inner wall of the high-speed planetary gear 40.
[0026] The low-speed stage includes: a low-speed input shaft 35, one end of which is connected to a high-speed planetary carrier 9 for transmission, and a low-speed sun gear 16 fixedly mounted on the other end. The low-speed sun gear 16 meshes with a low-speed planetary gear 41, realizing the transmission between the low-speed input shaft 35 and the low-speed planetary gear 41. The low-speed planetary gear 41 is mounted on the low-speed planetary gear shaft 34 via a needle roller bearing 7. The inner ring of the needle roller bearing 7 is fitted on the low-speed planetary gear shaft 34, and the outer ring is clearance-fitted with the low-speed planetary gear 41, reducing weight and adapting to low-speed operating conditions.
[0027] It also includes an output shaft 19, which is located inside the housing 42 at the end away from the high-speed input shaft 15. One end of the output shaft 19 is located inside the housing 42, and the other end extends out of the housing 42. One end of the output shaft 19 inside the housing 42 is fixedly connected to the low-speed planetary carrier 17 by an output shaft screw 18. The rotation of the low-speed planetary carrier 17 drives the output shaft 19 to rotate. The axial positioning of the output shaft 19 is achieved by two sets of back-to-back mounted first tapered roller bearings 2 and second tapered roller bearings 5.
[0028] The first tapered roller bearing 2 is located away from the low-speed planetary carrier 17, and the second tapered roller bearing 5 is located close to the low-speed planetary carrier 17. A second protrusion structure 27 is provided on the inner wall of the housing 42 between the first tapered roller bearing 2 and the second tapered roller bearing 5. The outer rings of the first tapered roller bearing 2 and the second tapered roller bearing 5 are respectively engaged with the two sides of the second protrusion structure 27 on the inner wall of the housing 42.
[0029] The outer ring of the first tapered roller bearing 2 is located near the low-speed planetary carrier 17 and is fitted into the recess of the second protrusion structure 27 on the side away from the low-speed planetary carrier 17. The inner ring of the first tapered roller bearing 2 is located away from the low-speed planetary carrier 17 and is pressed against the adjusting bushing 1.
[0030] The output shaft 19 has a laterally extending stepped structure at one end near the low-speed planetary carrier 17. The inner ring of the second tapered roller bearing 5 is fitted into the laterally extending stepped structure of the output shaft 19, and the outer ring of the second tapered roller bearing 5 is fitted into the recess on the side of the second protrusion 27 near the low-speed planetary carrier 17.
[0031] The first tapered roller bearing 2 and the second tapered roller bearing 5 are arranged back-to-back, and their specific installation position relationship is as follows. The first tapered roller bearing 2 and the second tapered roller bearing 5 consist of two bearings of the same model, with their inner ring small end faces facing each other and their outer rings facing outwards, forming a symmetrical outward-inclined contact angle. This structure ensures that the inner and outer ring raceways and the cone apexes of the rollers meet at the bearing centerline, guaranteeing pure rolling contact and reducing sliding friction. During installation, the first tapered roller bearing 2 and the second tapered roller bearing 5 are arranged at both ends of the output shaft 19, forming a large support span, enhancing system rigidity, and making it suitable for conditions subjected to alternating loads or bending moments. It also accommodates the thermal expansion of the shaft, preventing jamming. Furthermore, due to the installation of the adjusting bushing 1, the stepped structure extending laterally from the output shaft 19, and the second protrusion structure 27 of the housing 42, the axial and radial directions of the first tapered roller bearing 2 and the second tapered roller bearing 5 are stably limited and supported.
[0032] The housing 42 is also provided with a connecting flange 24 at one end of the output shaft 19. The connecting flange 24 has a through hole in the middle. The diameter of the outer wall of the connecting flange 24 is larger than that of the housing 42, and the diameter of the inner through hole is equal to the outer diameter of the output shaft 19. The connecting flange 24 is embedded in the housing 42 at the end of the output shaft 19, and its flange face forms a block on the housing 42. Its through hole is fitted onto the output shaft 19. The connecting flange 24 is also provided with a second extension 37 on the side near the low-speed planetary carrier 17. The second extension 37 is engaged in the gap between the housing 42 and the output shaft 19 at the end of the housing 42.
[0033] The inner wall of the connecting flange 24, at the end away from the low-speed planetary carrier 17, has a third step structure 30, and the inner wall at the end near the low-speed planetary carrier 17 has a fourth step structure 31. The output shaft 19, at the end away from the low-speed planetary carrier 17, has a fifth step structure 32. The third step structure 30 and the fifth step structure 32 are at the same height. The pressure plate 25 is disposed in the third step structure 30 and the fifth step structure 32. The pressure plate 25 is fixedly connected to the output shaft 19 by screws 23. Tightening the screws 23 will press the pressure plate 25 against the third step structure 30 and the fifth step structure 32. In section 2, since the gap between the third step structure 30 and the fifth step structure 32 is the gap between the output shaft 19 and the connecting flange 24, and the third step structure 30 and the fifth step structure 32 have the same height, the tightening of the pressure plate 25 can seal the gap between the output shaft 19 and the connecting flange 24, achieve a rigid axial connection between the output shaft 19 and the connecting flange 24 to resist loads, and also tighten the adjusting sleeve 1 that is stuck in the fourth step structure 31. The tightening of the adjusting sleeve 1 also achieves the tightening of the first tapered roller bearing 2.
[0034] One end of the adjusting bushing 1 is located inside the fourth step structure 31, and the other end is located at the top of the inner ring of the first tapered roller bearing 2 near the connecting flange 24. The third step structure 30 on the inner wall and the fifth step structure 32 of the output shaft 19 are fixed by a pressure plate 25 and screws 23.
[0035] It also includes a first sealing ring 20 disposed between the housing 42 and the second extension 37 of the connecting flange 24, and a second sealing ring 22 disposed in the gap between the output shaft 19 and the housing 42, and between the first tapered roller bearing 2 and the second tapered roller bearing 5. The second sealing ring 22 is disposed between the second protrusion structure 27 of the housing 42 and the gap between the output shaft 19. The second sealing ring 22 includes two interlocking lip-shaped sealing rings, which can achieve sealing in the rotational state. It separates the first tapered roller bearing 2 and the second tapered roller bearing 5, forming two relatively independent cavities.
[0036] One end of the cavity containing the first tapered roller bearing 2 is sealed by the adjusting bushing 1, the pressure plate 25, and the first sealing ring 20, while the other end is sealed by the second sealing ring 22, forming a first sealed cavity 38. One end of the second tapered roller bearing 5 is sealed by the second sealing ring 22, while the other end is connected to the inner cavity of the housing 42. The inner cavity of the housing 42 includes a two-stage planetary transmission system. The end of the housing 42 near the low-speed input shaft 15 is provided with a closed cover plate. The cover plate has a through hole for the low-speed input shaft 15 to pass through only, and a high-pressure sealing ring 13 is provided between the low-speed input shaft 15 and the cover plate of the housing 42 to form a seal. Thus, the second tapered roller bearing 5 and the cavity containing the two-stage planetary transmission system in the housing 42 together form a second sealed cavity 39.
[0037] The first sealing cavity 38 has a grease nipple 3 and a pressure vent cap 21 at the position on the housing 42 corresponding to the first tapered roller bearing 2. Grease is added through the grease nipple 3, and air is discharged through the pressure vent cap 21. The second sealing cavity 39 has a vent cap 4 and an oil window 6 at the position on the housing 42 corresponding to the second tapered roller bearing 5. The second tapered roller bearing 5 and the rest of the planetary transmission system of the reducer are lubricated by self-splashing oil. Oil is added to the oil window 6, and air is discharged through the vent cap 4. A pipeline connected to the outside is provided at the end of the housing 42 near the low-speed input shaft 15, and a magnetic plug 12 is installed on the pipeline. The lubricating oil in the first sealing cavity 38 and the second sealing cavity 39 are independent and not interconnected. At the high-speed input shaft 15, due to the high pressure generated by the high liquid surface on the input end oil seal, and the high input speed, a high-pressure sealing ring 13 is used to improve the reliability of the seal and the wear resistance of the high-speed input shaft 15.
[0038] A self-aligning ball bearing 14 and a high-pressure sealing ring 13 are installed between the high-speed input shaft 15 and the housing 42, and a blue paper baffle 11 is used to suppress vibration and oil leakage. The blue paper baffle 11 is designed at the high-speed input shaft 15 to prevent metal particles generated by gear running-in from entering the self-aligning ball bearing 14. The metal particles generated by gear running-in will be deposited on the surface of the magnetic plug 12 under the magnetic attraction of the pipe.
[0039] The inner wall of the housing 42 has a first protrusion structure 26 in the gap between the high-speed planetary carrier 9 and the low-speed planetary carrier 17. The low-speed planetary carrier 17 has a first extension 43 facing the high-speed planetary carrier 9. The outer side of the first extension 43 has a first step structure 28. The end of the first protrusion structure 26 facing the low-speed planetary carrier 17 has a second step structure 29. The inner and outer rings of the full roll bearing 8 are respectively disposed on the first step structure 29 of the first extension 43 and the second step structure 29 of the first protrusion structure 26. The full roll bearing 8, together with the first tapered roller bearing 2 and the second tapered roller bearing 5, provides axial limiting support for the low-speed planetary carrier 17.
[0040] Needle roller bearings 7 are compact, lightweight, and have thin inner walls with small diameters for individual needle rollers, saving considerable space and reducing the weight of rotating parts. However, they have poor load capacity and are prone to generating high frictional heat and centrifugal force, making them unsuitable for high-speed applications. Therefore, they are best suited for installation within the low-speed planetary carrier 17, where a greater number of needle rollers can be accommodated in the same space, thereby reducing the average friction area of each needle roller and extending the service life of the low-speed planetary gear 41's rotation structure.
[0041] Cylindrical roller bearing 10 has high radial and axial load capacity, low frictional heat generation and loss, high rigidity, and is suitable for high-speed applications. However, it is relatively large and heavy, and requires high-precision assembly. Therefore, it is suitable to be installed in the high-speed planetary carrier 9 to accommodate the high speed of the high-speed input shaft 15.
[0042] The inner wall of the housing 42 is also provided with two gear rings that mesh with the high-speed planetary gear 40 and the low-speed planetary gear 41 respectively. Preferably, the housing 42 is composed of several housing structures spliced together and fixed to each other with screws.
[0043] The transmission principle of this reducer is based on a two-stage planetary gear system, as detailed below:
[0044] The input to the high-speed transmission system is driven by a permanent magnet servo motor that rotates the high-speed input shaft 15, which in turn drives the high-speed sun gear 36. The transmission path is as follows: high-speed sun gear 36 to high-speed planetary gear 40, then to high-speed planetary carrier 9, and finally to low-speed input shaft 35.
[0045] The input to the low-speed transmission system is driven by the low-speed input shaft 35, which drives the low-speed sun gear 16. The transmission path is as follows: from the low-speed sun gear 16 to the low-speed planetary gear 41, then to the low-speed planetary carrier 17, and finally to the output shaft 19.
[0046] The planetary carrier is supported by the above structure. The high-speed planetary carrier 9 and the low-speed planetary carrier 17 are fixed by the first protrusion structure 26, the second protrusion structure 27, the cylindrical roller bearing 10, and the needle roller bearing 7, which reduces the gear meshing load and ensures transmission stability.
[0047] The first tapered roller bearing 2 and the second tapered roller bearing 5 are installed back to back to bear the combined load of the output shaft 19, avoiding axial displacement during transmission that could lead to meshing misalignment, and better suppressing axial load offset of the output shaft 19.
[0048] Through a two-stage planetary gear reduction, the high input speed is gradually reduced, the torque is multiplied, and finally the output shaft 19 obtains low speed and high torque, which meets the power characteristics required for monorail drive.
[0049] The above description is merely a specific embodiment of this utility model, but the protection scope of this utility model is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the technical scope disclosed in this utility model, based on the technical solution and novel concept of this utility model, should be included within the protection scope of this utility model.
Claims
1. A monorail crane drive reducer, comprising a housing, a high-speed input shaft, a low-speed input shaft, a high-speed planetary carrier, and a low-speed planetary carrier coaxially disposed within the housing, a plurality of high-speed planetary gears and a plurality of low-speed planetary gears respectively disposed on the high-speed planetary gear shaft of the high-speed planetary carrier and the low-speed planetary gear shaft of the low-speed planetary carrier, one end of the low-speed input shaft being connected to the high-speed planetary carrier and the other end having a low-speed sun gear meshing with the low-speed planetary gears, and one end of the high-speed input shaft having a high-speed sun gear meshing with the high-speed planetary gears, characterized in that, The high-speed planetary gear and the high-speed planetary gear shaft are connected by cylindrical roller bearings, and the low-speed planetary gear and the low-speed planetary gear shaft are connected by needle roller bearings. The inner wall of the housing is provided with a first protrusion structure in the gap between the high-speed planetary carrier and the low-speed planetary carrier. The low-speed planetary carrier is provided with a first extension on the side facing the high-speed planetary carrier. The outer side of the end of the first extension is provided with a first step structure. The end of the first protrusion structure facing the low-speed planetary carrier is provided with a second step structure. The inner ring and outer ring of the full roller bearing are respectively set on the first step structure of the first extension and the second step structure of the first protrusion structure. The output shaft is connected to the end of the low-speed planetary carrier furthest from the high-speed planetary carrier. A connecting flange is provided at the end of the housing near the output shaft. The connecting flange has a second extension on the side near the housing. The outer diameter of the second extension is the same as the inner diameter of the end of the housing. The second extension of the connecting flange is engaged inside the end of the housing.
2. The monorail crane drive reducer as described in claim 1, characterized in that, The output shaft and the housing are provided with a first tapered roller bearing and a second tapered roller bearing arranged coaxially. The first tapered roller bearing is located at the end away from the low-speed planetary carrier, and the second tapered roller bearing is located at the end closer to the low-speed planetary carrier. The first tapered roller bearing and the second tapered roller bearing are installed back to back.
3. The monorail crane drive reducer as described in claim 2, characterized in that, The inner wall of the housing is provided with a second protrusion structure between the first tapered roller bearing and the second tapered roller bearing, and the outer rings of the first tapered roller bearing and the second tapered roller bearing are respectively arranged on both sides of the second protrusion structure.
4. A monorail crane drive reducer as described in claim 2, characterized in that, A first sealing ring is provided between the housing and the output shaft, and between the first tapered roller bearing and the second tapered roller bearing, forming a first sealed cavity inside the housing that is isolated from the first tapered roller bearing; A second sealing ring is provided between the second extension of the connecting flange and the inner wall of the housing, forming a second sealed cavity inside the housing that includes only the output shaft and the first tapered roller bearing; The housing is provided with an oil filler and a pressure vent cap at the location corresponding to the first tapered roller bearing, a vent cap at the location corresponding to the second tapered roller bearing, and an oil window at the location corresponding to the low-speed planetary carrier.
5. A monorail crane drive reducer as described in claim 2, characterized in that, The inner wall of the connecting flange at the end away from the low-speed planetary carrier has a third step structure, and the inner wall at the end closer to the low-speed planetary carrier has a fourth step structure. The output shaft is provided with a fifth step structure at the end away from the low-speed planetary carrier. The third step structure and the fifth step structure are at the same height. The pressure plate is set in the third step structure and the fifth step structure. The pressure plate is connected to the output shaft by screws. One end of the adjusting bushing is located inside the fourth step structure, and the other end is located at the top of the inner ring of the first tapered roller bearing near the connecting flange.
6. A monorail crane drive reducer as described in claim 1, characterized in that, The high-speed input shaft and the housing are fitted with a self-aligning ball bearing, and a high-pressure sealing ring is provided between the high-speed input shaft and the housing.
7. A monorail crane drive reducer as described in claim 1, characterized in that, A blue paper baffle is provided between the high-speed input shaft and the housing.