A super winding hoist reduction gear for a crane

Abstract

The application discloses a super-lifting hoist speed reducer matched with a crane and belongs to the technical field of arm support type crane components. The speed reducer comprises a winding drum, three-stage planetary gear transmission is arranged in the drum cavity of the winding drum, a transmission structure with large torque transmission is used for an output stage, transmission structures with small torque transmission are used for an input stage and an intermediate stage, the input stage, the intermediate stage and a rear support shaft can share part of axial installation space through layout design, the space requirement in the axial direction is further reduced, a small displacement motor can be matched to output a larger speed ratio in the limited assembly space of the crane arm support, and the super-lifting function requirement of the crane is met.

Description

Technical Field

[0001] This invention belongs to the technical field of boom-type crane components, and particularly relates to a super-lift winch reducer used in cranes. Background Technology

[0002] A superlift is a crucial crane component installed on the crane's boom to improve the relationship between the boom and the wire rope, creating more triangular geometric relationships. By improving the parallel geometry of the boom and wire ropes and adding an extra counterweight at the rear of the crane, the superlift boom connects to the counterweight, forming a double-triangular stability structure. This increases the overall boom stability, thereby improving the crane's performance. Superlifts are primarily used on large cranes to achieve the theoretically designed lifting capacity, reaching over 105% of the maximum load.

[0003] The super-lift winch is a winch used in the super-lift operation of large crawler cranes. When the motor drives the winch to rotate, the load of the super-lift winch is only the boom and its accessories. When the crane is lifting a heavy object, the super-lift winch does not rotate; the wire rope pulls the winch, and at this time, the super-lift winch will be subjected to a large static load. In summary, the super-lift winch requires a static load much greater than the dynamic load. The super-lift winch is installed on the boom of the crane, with limited axial space, so conventional winches cannot be directly adapted. Due to the limited axial space, the small transmission part can only withstand a relatively low load. Therefore, it is necessary to design a super-lift winch reducer for cranes.

[0004] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this disclosure, and therefore may include information that does not constitute prior art. Summary of the Invention

[0005] Through research, the inventors discovered that, due to the influence of the operating environment of the super-lift winch, the super-lift winch requires a static load that is much greater than the dynamic load. The super-lift winch is installed on the boom of the crane arm, and the axial space is small. Therefore, it cannot be directly adapted to a conventional winch. Due to the limited axial space, the small transmission part can only withstand a low load.

[0006] In view of at least one of the above technical problems, this disclosure provides a super-lift winch reducer for use with cranes, and the specific technical solution is as follows: A super-lift winch reducer for use with cranes. The device includes a drum, which has a cavity along its axis in the middle. One end of the cavity is provided with a large annular bearing seat, and the inner end of the large bearing seat is provided with a large internal gear ring. The inner end of the large internal gear ring is provided with a small internal gear ring. The inner end of the small internal gear ring is provided with a rear cover, and the center of the outer surface of the rear cover is provided with a top shaft. The inner cavity of the large bearing housing is axially equipped with two opposing rolling bearings. The inner ring of the rolling bearing is fitted with a flange, and the flange has a through cavity along the axis in the middle. The inner end face of the flange has a ring array of several planetary gear shafts. Each planetary gear shaft is equipped with an output stage planetary gear through a bearing. The output stage planetary gear meshes with the large internal gear ring. The cavity contains a central gear shaft, which includes a central shaft and an input-stage central gear at its inner end. The inner end face of the central gear shaft is in coaxial contact with the top shaft. An input-stage planetary carrier is fitted inside the central gear shaft, and several input-stage planetary gears are arranged in a circular array on the input-stage planetary carrier. The input-stage planetary gears are connected to the input-stage planetary carrier via bearings. One side of each input-stage planetary gear meshes externally with the input-stage central gear, and the other side meshes internally with the small internal gear ring. An output-stage central gear is fitted on the central shaft, and the output-stage central gear meshes externally with the output-stage planetary gears. An intermediate-stage planetary carrier is fitted inside the output-stage central gear, and several intermediate-stage planetary gears are arranged in a circular array on the intermediate-stage planetary carrier. The intermediate-stage planetary gears are connected to the intermediate-stage planetary carrier via bearings. An intermediate-stage central gear is fitted on the central shaft between the output-stage central gear and the input-stage central gear. One side of each intermediate-stage planetary gear meshes internally with the small internal gear ring, and the other side meshes externally with the intermediate-stage central gear. The outer end of the cavity is provided with a countersunk hole concentric with the cavity, and a brake acting on the intermediate stage center wheel is disposed in the countersunk hole. The brake is provided with an air passage. A flexible sealing plate assembly is disposed on the outside of the brake. A connecting shaft is sleeved on the outer end of the center shaft. A front support shaft is disposed on the outside of the cavity. A transmission shaft hole is disposed in the middle of the front support shaft. The other end of the cylinder is equipped with a brake and a rear support is provided on the outside. The rear support is connected to a rear support shaft through a roller self-aligning bearing. The rear support shaft has a through hole in the middle and an end cap is detachably connected to the outside of the through hole.

[0007] In some embodiments of this disclosure, a sealing ring I is provided between the large bearing housing and the large internal gear ring, a sealing ring II is provided between the large internal gear ring and the small internal gear ring, a sealing ring III is provided between the small internal gear ring and the rear cover, a brake sealing assembly I is provided between the flexible sealing plate assembly and the flange, a hole retaining ring is provided between the front support shaft and the flexible sealing plate assembly, and a sealing ring IV is provided between the front support shaft and the flange.

[0008] In some embodiments of this disclosure, the rolling bearing is a tapered roller bearing, and the rolling bearing is axially limited by a nut disposed on the outer surface of the flange.

[0009] In some embodiments of this disclosure, brake teeth are evenly distributed on the side of the outer end of the output stage center wheel, and the brake is a wet multi-plate friction clutch that is used in conjunction with the brake teeth.

[0010] In some embodiments of this disclosure, the flexible sealing plate assembly includes a spring pressure plate and a piston member. A coil spring is disposed between the spring pressure plate and the piston member. The outer surface of the spring pressure plate contacts the inner surface of the front support shaft. A retaining ring for a hole is disposed between the spring pressure plate and the front support shaft. The inner surface of the piston member acts on the wet multi-plate friction clutch. A brake sealing assembly II is disposed between the outer side of the piston member and the flange.

[0011] In some embodiments of this disclosure, the inner end of the air passage is connected to the countersunk hole, and the outer end of the air passage includes a fluid pipe assembly, which includes a hollow tube, and the end of the hollow tube is provided with a vent plug.

[0012] In some embodiments of this disclosure, the drum includes a roller, the drum cavity is disposed inside the roller, and webs are provided on opposite sides of the roller. The webs are ratchet structures, which can be tightened by a hydraulic cylinder or pawl during over-lifting operations to prevent the winch from reversing.

[0013] In some embodiments of this disclosure, the hollow tube is an L-shaped rigid tube, and the hollow tube faces the stopping direction of the ratchet of the web. By improving the airflow path and setting the L-shaped rigid tube, when the drum stops rotating, the vent plug at the far end of the hollow tube remains at the highest point of the airflow path. When the hoisting reducer is stationary, the L-shaped rigid tube is in a horizontal position. When the hoisting reducer rotates, the hollow tube is installed horizontally to the right or left according to the rotation direction, i.e., the stopping direction of the ratchet of the web. This ensures that after the reducer moves with the frame, the vent plug at the far end of the hollow tube remains at the highest point of the airflow path.

[0014] In some embodiments of this disclosure, an end face bearing is adapted between the end faces of the connecting shaft and the central shaft to separate the connecting shaft from the central shaft and to provide axial positioning.

[0015] In some embodiments of this disclosure, a grease cup is provided on one side of the self-aligning roller bearing.

[0016] Compared with the prior art, the present invention has the following beneficial effects: The three-stage planetary gear transmission of the present invention is convenient for use in small axial assembly spaces on the boom and can achieve a large speed ratio with a small displacement motor. The output stage uses a transmission structure with a larger torque transmission, while the input stage and intermediate stage use a transmission structure with a smaller torque transmission. Through layout design, the input stage, intermediate stage and rear support shaft can share part of the axial installation space, further reducing the axial space requirement. Two opposing rolling bearings are axially arranged in the inner cavity of the large bearing housing, allowing the large bearing housing to bear more load. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of embodiment 3 of the structure of the present invention; Figure 2 for Figure 1 A schematic diagram of the vertical cross-section; Figure 3 for Figure 2 A magnified view of part A in the middle; The following are the labeling instructions in the diagram: 1. Drum; 11. Web plate; 21. Large bearing housing; 22. Large internal gear ring; 23. Small internal gear ring; 24. Rear cover; 241. Top shaft; 31. Rolling bearing; 32. Roller self-aligning bearing; 4. Flange; 41. Planetary gear shaft; 42. Output stage planetary gear; 5. Center gear shaft; 51. Center shaft; 511. Connecting shaft; 52. Input stage center gear; 521. Input stage planetary carrier; 522. Input stage planetary gear; 53. Output stage center gear; 54. Intermediate stage center gear; 541. Intermediate stage planetary carrier; 542. Intermediate stage planetary gear; 61. Brake; 62. Air passage; 621. Hollow tube; 622. Vent plug; 63. Flexible sealing plate assembly; 71. Front support shaft; 72. Rear support; 73. Rear support shaft; 74. End cover. Detailed Implementation

[0018] To better understand the purpose, structure, and function of this invention, the technical solutions in the embodiments of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this invention, and not all embodiments.

[0019] The serial numbers assigned to components in this document are solely for distinguishing the objects described and have no sequential or technical meaning. The term "connection" in this disclosure, unless otherwise specified, includes both direct and indirect connections. In the description of this application, it should be understood that directional terms such as "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are for ease of description only and do not indicate or imply that the device or unit referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0020] As shown in the attached diagram. Figures 1 to 3 As shown, a super-lift winch reducer for use with cranes is designed. The device includes a drum 1, with a cavity along its central axis. One end of the cavity is fitted with a large annular bearing seat 21, which is detachably connected to the cavity. A large internal gear ring 22 is fitted to the inner end of the bearing seat 21, and the bearing seat 21 and the large internal gear ring 22 are detachably connected. A small internal gear ring 23 is fitted to the inner end of the large internal gear ring 22, and the large internal gear ring 22 and the small internal gear ring 23 are detachably connected. A rear cover 24 is fitted to the inner end of the small internal gear ring 23, and the small internal gear ring 23 and the rear cover 24 are detachably connected. A top shaft 241 is located at the center of the outer surface of the rear cover 24, and the rear cover 24 and the top shaft 241 are detachably connected. The inner cavity of the large bearing housing 21 is axially fitted with two opposing rolling bearings 31. The outer ring of the large bearing housing 21 and the rolling bearing 31 are interference-fitted. The inner ring of the rolling bearing 31 is fitted with a flange 4, and the inner ring of the rolling bearing 31 is interference-fitted with the flange 4. By axially fitting two opposing rolling bearings in the inner cavity of the large bearing housing 21, the large bearing housing 21 can bear more load. The flange 4 has a through cavity along the axis in the middle. The inner end face of the flange 4 has a ring array of several planetary gear shafts 41. Each planetary gear shaft 41 is fitted with an output stage planetary gear 42 through a bearing. This bearing is a rolling bearing. The output stage planetary gear 42 meshes with the large internal gear ring 22. The cavity contains a central gear shaft 5, which includes a central shaft 51. An input-stage central gear 52 is located at the inner end of the central shaft 51. The inner end face of the central gear shaft 5 is coaxially contacted with the top shaft 241. An input-stage planetary support 521 is fitted inside the central gear shaft 5. Several input-stage planetary gears 522 are arranged in a circular array on the input-stage planetary support 521. The input-stage planetary gears 522 are connected to the input-stage planetary support 521 via bearings. One side of each input-stage planetary gear 522 meshes externally with the input-stage central gear 52, and the other side meshes internally with the small internal gear ring 23. An output-stage central gear 53 is fitted inside the central shaft 51, and it meshes externally with the output-stage planetary gears 42. An intermediate-stage planetary carrier 541 is fitted inside the output-stage central gear 53. The intermediate planetary carrier 541 has several intermediate planetary gears 542 arranged in a ring, and the intermediate planetary gears 542 are connected to the intermediate planetary carrier 541 through bearings; an intermediate central gear 54 is provided on the central shaft 51 between the output central gear 53 and the input central gear 52; one side of the intermediate planetary gear 542 meshes internally with the small internal gear ring 23, and the other side meshes externally with the intermediate central gear 54; the three-stage planetary gear transmission of the present invention is convenient for use in the small axial assembly space on the boom, and can achieve a large speed ratio with a small displacement motor; the output stage uses a transmission structure with a large torque transmission, while the input stage and intermediate stage use a transmission structure with a small torque transmission. Through layout design, the input stage, intermediate stage and rear support shaft can share part of the axial installation space, further reducing the axial space requirement; The outer end of the cavity is concentrically provided with a countersunk hole, and a brake 61 acting on the intermediate stage center wheel 54 is disposed in the countersunk hole. This brake is used to provide static load bearing. The brake 61 is provided with an air passage 62. A flexible sealing plate assembly 63 is disposed on the outside of the brake 61. A connecting shaft 511 is sleeved on the outer end of the center shaft 51. A front support shaft 71 is disposed on the outside of the cavity. A transmission shaft hole is disposed in the middle of the front support shaft 71. The other end of the cylindrical cavity is provided with a rear support 72, and the rear support 72 is connected to a rear support shaft 73 through a roller self-aligning bearing 32. The rear support shaft 73 has a through hole in the middle, and an end cap 74 is detachably connected to the outside of the through hole. A three-stage planetary gear transmission is arranged inside the drum cavity of the drum 1. The output stage uses a transmission structure with a larger torque, while the input stage and intermediate stage use transmission structures with a smaller torque. Through the layout design, the input stage, intermediate stage and the rear support shaft 73 can share part of the axial installation space, further reducing the axial space requirement. It is possible to achieve a larger speed ratio with a small displacement motor in the limited assembly space of the crane boom, so as to meet the super-lift function requirements of the crane.

[0021] The above embodiments illustrate three examples of implementing the above technical solutions: Example 1 discloses a super-lift winch reducer for use with a crane, wherein: The system includes a drum 1, which comprises a roller. A drum cavity is located inside the roller. Two opposing webs 11 are provided on either side of the roller. Each web 11 has a ratchet structure, which can be tightened by a hydraulic cylinder or pawl during over-lifting operations to prevent reverse winding. One end of the drum cavity is fitted with a large annular bearing seat 21, and the drum cavity and the large bearing seat 21 are detachably connected. A large internal gear ring 22 is fitted to the inner end of the large bearing seat 21. The large internal gear ring 22 is detachably connected; a small internal gear ring 23 is fitted to the inner end of the large internal gear ring 22, and the large internal gear ring 22 and the small internal gear ring 23 are detachably connected; a rear cover 24 is fitted to the inner end of the small internal gear ring 23, and the small internal gear ring 23 and the rear cover 24 are detachably connected; a top shaft 241 is provided at the center of the outer surface of the rear cover 24, and the rear cover 24 and the top shaft 241 are detachably connected, wherein the detachable connection can be a screw connection; The inner cavity of the large bearing housing 21 is axially fitted with two opposing rolling bearings 31. The outer ring of the large bearing housing 21 and the rolling bearing 31 are interference-fitted. The inner ring of the rolling bearing 31 is fitted with a flange 4, and the inner ring of the rolling bearing 31 is interference-fitted with the flange 4. By axially fitting two opposing rolling bearings in the inner cavity of the large bearing housing 21, the large bearing housing 21 can bear more load. The flange 4 has a through cavity along the axis in the middle. The inner end face of the flange 4 has a ring array of several planetary gear shafts 41. Each planetary gear shaft 41 is fitted with an output stage planetary gear 42 through a bearing. This bearing is a rolling bearing. The output stage planetary gear 42 meshes with the large internal gear ring 22. The cavity contains a central gear shaft 5, which includes a central shaft 51. An input-stage central gear 52 is located at the inner end of the central shaft 51. The inner end face of the central gear shaft 5 is coaxially contacted with the top shaft 241. An input-stage planetary support 521 is fitted inside the central gear shaft 5. Several input-stage planetary gears 522 are arranged in a circular array on the input-stage planetary support 521. The input-stage planetary gears 522 are connected to the input-stage planetary support 521 via bearings. One side of each input-stage planetary gear 522 meshes externally with the input-stage central gear 52, and the other side meshes internally with the small internal gear ring 23. An output-stage central gear 53 is fitted inside the central shaft 51, and it meshes externally with the output-stage planetary gears 42. An intermediate-stage planetary carrier 541 is fitted inside the output-stage central gear 53. The intermediate planetary carrier 541 has several intermediate planetary gears 542 arranged in a ring, and the intermediate planetary gears 542 are connected to the intermediate planetary carrier 541 through bearings; an intermediate central gear 54 is provided on the central shaft 51 between the output central gear 53 and the input central gear 52; one side of the intermediate planetary gear 542 meshes internally with the small internal gear ring 23, and the other side meshes externally with the intermediate central gear 54; the three-stage planetary gear transmission of the present invention is convenient for use in the small axial assembly space on the boom, and can achieve a large speed ratio with a small displacement motor; the output stage uses a transmission structure with a large torque transmission, while the input stage and intermediate stage use a transmission structure with a small torque transmission. Through layout design, the input stage, intermediate stage and rear support shaft can share part of the axial installation space, further reducing the axial space requirement; The outer end of the through cavity is concentrically provided with a countersunk hole, and a brake 61 acting on the intermediate stage center wheel 54 is disposed in the countersunk hole. This brake is used to provide static load bearing. The brake 61 is provided with an air passage 62. A flexible sealing plate assembly 63 is disposed on the outside of the brake 61. A connecting shaft 511 is sleeved on the outer end of the center shaft 51. The outer end of the center shaft 51 and the connecting shaft 511 are circumferentially linked through a spline. A front support shaft 71 is detachably connected to the outside of the through cavity, which can be a screw connection. A drive shaft hole is provided in the middle of the front support shaft 71. The other end of the cylindrical cavity is provided with a rear support 72, and the rear support 72 is connected to a rear support shaft 73 through a roller self-aligning bearing 32. The rear support shaft 73 has a through hole in the middle, and an end cap 74 is detachably connected to the outside of the through hole. A three-stage planetary gear transmission is arranged inside the drum cavity of the drum 1. The output stage uses a transmission structure with a large torque, while the input stage and intermediate stage use transmission structures with a small torque. Through the layout design, the input stage, intermediate stage and the rear support shaft 73 can share part of the axial installation space, further reducing the axial space requirement. It is possible to achieve a large speed ratio with a small displacement motor in the limited assembly space of the crane boom, so as to meet the super-lift function requirements of the crane. Based on the above scheme, a sealing ring I is provided between the large bearing housing 21 and the large internal gear ring 22; a sealing ring II is provided between the large internal gear ring 22 and the small internal gear ring 23; a sealing ring III is provided between the small internal gear ring 23 and the rear cover 24; a brake sealing assembly I is provided between the flexible sealing plate assembly 63 and the flange 4; a retaining ring for holes is provided between the front support shaft 71 and the flexible sealing plate assembly 63; and a sealing ring IV is provided between the front support shaft 71 and the flange 4. Sealing rings I, II, III, or IV can be rubber sealing rings, such as O-ring structures, or sealing rings of other cross-sectional shapes for the purpose of achieving airtight sealing. The brake sealing assembly I can be an oil seal structure, a mechanical component for sealing grease, which connects the lubricated parts in the transmission components to the outlet. Force components are isolated to prevent lubricant leakage; the rolling bearing 31 is a tapered roller bearing, which facilitates assembly and helps reduce the runout of the flange 4, making the operation of this invention smoother. The rolling bearing 31 is axially limited by a nut on the outer surface of the flange 4. The outer surface of the flange 4 is provided with an external thread that matches the nut. The inner cavity of the large bearing seat 21 is provided with a spacer step, and the two rolling bearings 31 are respectively assembled on both sides of the spacer step; brake teeth are evenly distributed on the side of the outer end of the output stage center wheel 53, and the brake 61 is used with the brake teeth; a grease cup is provided on one side of the self-aligning roller bearing 32. During use, grease can be added to the grease cup to lubricate the self-aligning roller bearing 32 and effectively prevent the self-aligning roller bearing 32 from overheating.

[0022] This embodiment includes two functional aspects: dynamic torque transmission and static load bearing. Dynamic torque transmission is the conventional function of the winch, where the winch rotates forward and backward under the drive of the motor, raising and lowering the crane boom via the wire rope. Static load bearing refers to the situation where, after the overlift winch reaches its position, the brake locks; the ratchet engages to prevent the winch from rotating backward; the crane begins its overlift operation, and the overlift winch experiences a significant static load tension. The dynamic torque or power transmission process can be analyzed as a three-stage transmission, consisting of a two-stage differential planetary gear transmission and a quasi-planetary gear transmission. The input stage and intermediate stage are differential planetary gear transmissions, while the output stage is a quasi-planetary gear transmission. Its transmission characteristics are as follows: the input power is transmitted to the first-stage transmission mechanism for the first power split; then it is transmitted to the second-stage transmission mechanism for the second power split; at the same time, the second-stage transmission mechanism transmits part of the power to the third-stage transmission mechanism; after conversion by the third-stage transmission mechanism, the output power is combined with the power directly output by the first two stages for output; most of the power of the differential planetary gear transmission is split to the next stage transmission mechanism, and a small part of the power is directly output; the static load of the super-lift can be analyzed as follows: when the super-lift winch rotates to the position, the ratchet locking structure locks the drum in one direction; during the super-lift lifting process, the tension is transmitted to the drum through the wire rope, and then to the frame through the large bearings on both sides.

[0023] Embodiment 2 discloses a super-lift winch reducer for a crane. This embodiment is based on Embodiment 1. Brake teeth are evenly distributed on the outer side of the output stage center wheel 53. The brake 61 is a wet multi-plate friction clutch that engages with the brake teeth. The flexible sealing plate assembly 63 includes a spring pressure plate and a piston. A coil spring is disposed between the spring pressure plate and the piston. The outer surface of the spring pressure plate contacts the inner surface of the front support shaft 71. A retaining ring for a hole is disposed between the spring pressure plate and the front support shaft. The piston... The inner surface acts on the wet multi-plate friction clutch. A brake sealing assembly II is provided between the outer side of the piston and the flange 4. The brake sealing assembly II can be an oil seal structure, a mechanical component for sealing grease. It isolates the lubricated parts in the transmission components from the output parts to prevent lubricating oil leakage. The inner end of the air passage 62 is connected to the counterbore. The outer end of the air passage includes a fluid pipe assembly. The fluid pipe assembly includes a hollow pipe 621. The end of the hollow pipe 621 is provided with a vent plug 622.

[0024] like Figures 1 to 3 As shown, Embodiment 3 discloses a super-lift winch reducer for use with a crane. This embodiment is based on Embodiment 2. Because the diameter of the drum 1 is relatively large, in order to reduce weight and increase strength, the web 11 is thinned, and the outer side is equipped with... The outer surface of the drum is equipped with a guide wire groove to facilitate smoother automated winding and unwinding of the steel cable for the super-lift winch. The hollow tube 621 is an L-shaped rigid tube, which can be a right-angle equilateral bend tube, a right-angle unequal bend tube, a rounded equilateral bend tube, or a rounded equilateral bend tube, etc. The hollow tube 621 faces the locking direction of the ratchet of the web plate 11. The super-lift winch mounting arm will have a certain angle adjustment depending on the usage, that is, the super-lift winch and its support will rotate at a certain angle, which is generally no more than 90 degrees. Therefore, the fixed vent plug 622 position may leak oil due to winch rotation. Therefore, ensuring that there is no oil leakage from the vent plug 622 is a new requirement for the super-lift winch. By improving the airflow path 62, a new airflow path is set... The L-shaped rigid tube ensures that when the drum 1 stops rotating, the vent plug 622 at the opening of the hollow tube 621 at the far end remains at the highest point of the airflow path 62. When the hoisting reducer is stationary, the L-shaped rigid tube is in a horizontal position. When the hoisting reducer rotates, depending on the direction of rotation, i.e., the stopping direction of the ratchet of the web plate 11, the hollow tube 621 is installed horizontally to the right or left, so that after the reducer moves with the frame, the vent plug 622 at the opening of the hollow tube at the far end remains at the highest point of the airflow path 62. An end face bearing is adapted between the end face of the connecting shaft 511 and the end face of the central shaft 51 to separate the connecting shaft from the central shaft and provide axial limiting.

[0025] It is understood that the present invention has been described through some embodiments, and those skilled in the art will recognize that various changes or equivalent substitutions can be made to these features and embodiments without departing from the spirit and scope of the invention. Furthermore, under the teachings of the present invention, these features and embodiments can be modified to adapt to specific situations and materials without departing from the spirit and scope of the invention. Therefore, the present invention is not limited to the specific embodiments disclosed herein, and all embodiments falling within the scope of the claims of this application are within the protection scope of the present invention.

Claims

1. A super-lift winch reducer for use with a crane, characterized in that: The device includes a drum (1), which has a cavity along its axis in the middle. One end of the cavity is provided with a large annular bearing seat (21), and the inner end of the large bearing seat (21) is provided with a large internal gear ring (22). The inner end of the large internal gear ring (22) is provided with a small internal gear ring (23). The inner end of the small internal gear ring (23) is provided with a rear cover (24), and the center of the outer surface of the rear cover (24) is provided with a top shaft (241). The inner cavity of the large bearing housing (21) is axially equipped with two opposing rolling bearings (31). The inner ring of the rolling bearings (31) is fitted with a flange (4). The flange (4) has a through cavity along the axis in the middle. The inner end face of the flange (4) has a ring array of several planetary gear shafts (41). Each planetary gear shaft (41) is equipped with an output stage planetary gear (42) through a bearing. The output stage planetary gear (42) meshes with the large internal gear ring (22). The cavity is provided with a central gear shaft (5), which includes a central shaft (51). The inner end of the central shaft (51) is provided with an input stage central gear (52). The inner end face of the central gear shaft (5) is in coaxial contact with the top shaft (241). An input stage planetary support (521) is sleeved on the inner side of the central gear shaft (5). Several input stage planetary gears (522) are arranged in a ring on the input stage planetary support (521). The input stage planetary gears (522) are connected to the input stage planetary support (521) through bearings. One side of the input stage planetary gear (522) meshes externally with the input stage central gear (52), and the other side meshes internally with the small internal gear ring (23). The central shaft (51) The input stage is equipped with an output stage center gear (53), which meshes externally with the output stage planetary gear (42); an intermediate stage planetary carrier (541) is fitted on the inner end of the output stage center gear (53), and several intermediate stage planetary gears (542) are arranged in a ring on the intermediate stage planetary carrier (541), and the intermediate stage planetary gears (542) are connected to the intermediate stage planetary carrier (541) by bearings; an intermediate stage center gear (54) is equipped on the central shaft (51) between the output stage center gear (53) and the input stage center gear (52); one side of the intermediate stage planetary gear (542) meshes internally with the small internal gear ring (23), and the other side meshes externally with the intermediate stage center gear (54); The outer end of the cavity is provided with a countersunk hole concentric with the cavity, and a brake (61) acting on the intermediate stage center wheel (54) is provided in the countersunk hole. The brake (61) is provided with an air passage (62). A flexible sealing plate assembly (63) is provided on the outside of the brake (61). A connecting shaft (511) is sleeved on the outer end of the center shaft (51). A front support shaft (71) is provided on the outside of the cavity. A transmission shaft hole is provided in the middle of the front support shaft (71). The other end of the cylindrical cavity is provided with a rear support (72), and the rear support (72) is connected to a rear support shaft (73) through a roller self-aligning bearing (32). The rear support shaft (73) has a through hole in the middle, and an end cap (74) is detachably connected to the outside of the through hole. Brake teeth are evenly distributed on the outer side of the output stage center wheel (53), and the brake (61) is a wet multi-plate friction clutch that is used with the brake teeth. The inner end of the air passage (62) is connected to the countersunk hole, and the outer end of the air passage includes a fluid pipe assembly. The fluid pipe assembly includes a hollow pipe (621), and the end of the hollow pipe (621) is provided with a vent plug (622). The drum (1) includes a roller, the drum cavity is located inside the roller, and the two sides of the roller are provided with web plates (11), the web plates (11) are ratchet structures; The hollow tube (621) is an L-shaped rigid tube, and the hollow tube (621) is oriented toward the stopping direction of the ratchet of the web plate (11).

2. The super-lift winch reducer for cranes according to claim 1, characterized in that, A sealing ring I is provided between the large bearing housing (21) and the large internal gear ring (22); a sealing ring II is provided between the large internal gear ring (22) and the small internal gear ring (23); a sealing ring III is provided between the small internal gear ring (23) and the rear cover (24); a brake sealing assembly I is provided between the flexible sealing plate assembly (63) and the flange (4); a hole retaining ring is provided between the front support shaft (71) and the flexible sealing plate assembly (63); and a sealing ring IV is provided between the front support shaft (71) and the flange (4).

3. The super-lift winch reducer for cranes according to claim 1, characterized in that, The rolling bearing (31) is a tapered roller bearing, and the rolling bearing (31) is axially limited by a nut provided on the outer surface of the flange (4).

4. The super-lift winch reducer for cranes according to claim 2, characterized in that, The flexible sealing plate assembly (63) includes a spring pressure plate and a piston. A coil spring is provided between the spring pressure plate and the piston. The outer surface of the spring pressure plate contacts the inner surface of the front support shaft (71). A retaining ring for a hole is provided between the spring pressure plate and the front support shaft. The inner surface of the piston acts on the wet multi-plate friction clutch. A brake sealing assembly II is provided between the outer side of the piston and the flange (4).

5. The super-lift winch reducer for cranes according to claim 1, characterized in that, An end face bearing is adapted between the end face of the connecting shaft (511) and the end face of the central shaft (51).

6. The super-lift winch reducer for a crane according to claim 1, characterized in that, The self-aligning roller bearing (32) is provided with a grease cup on one side.

Images