Compact hydraulic winch with large tonnage and high speed ratio

Abstract

The utility model relates to the technical field of winches, in particular to a large-tonnage high-speed-ratio compact hydraulic winch, which comprises a winding drum body with a built-in planetary speed change mechanism, and a left lateral vertical seat and a right lateral vertical seat are symmetrically mounted on the left side and the right side of the winding drum body respectively. The bottom of the left lateral vertical seat and the bottom of the right lateral vertical seat are both fixed to the top of a horizontal mounting seat, a first speed change unit is mounted on the right side of the right lateral vertical seat, a second speed change unit is mounted on the left side of the left lateral vertical seat, and the output end of the second speed change unit is connected with a planetary speed change mechanism in the winding drum body. And the input end of the first speed change unit is connected with a large-tonnage hydraulic motor. Compared with a traditional hydraulic winch, the compact hydraulic winch with the large tonnage and the high speed ratio has the advantages that the speed ratio is better, speed regulation and speed reduction can be better achieved according to the hoisting requirement, and the compact hydraulic winch is effectively suitable for various complex working conditions.

Description

Technical Field

[0001] The utility model relates to the technical field of winches, in particular to a compact hydraulic winch with large tonnage and high speed ratio. Background Art

[0002] A hydraulic winch is a type of lifting equipment powered and controlled by a hydraulic system. As an efficient and reliable lifting equipment, it plays an important role in many fields and is often used for lifting and moving heavy objects, such as lifting and suspending construction materials, equipment or heavy components.

[0003] Traditional hydraulic winches usually use a multi-stage speed change structure to achieve the purpose of changing the speed ratio, but they generally use an internal planetary speed change mechanism built into the drum to achieve appropriate speed ratio changes. However, when dealing with some usage scenarios with special needs, the traditional built-in deceleration method inside the drum cannot meet the high speed ratio requirements.

[0004] For example, a prior patent application document with patent application number CN202323194829.3 discloses a low-speed, high-pull hydraulic winch, whose main structure includes a motor connecting disc, a brake housing, a low-speed, high-torque motor, a planetary speed change mechanism placed inside the drum body, and other key components.

[0005] It can be seen from the records of the above patents that due to the limited speed range of the low-speed ratio hydraulic winch, it is difficult to meet the requirements in applications that require precise speed control; it is also easy to cause high energy consumption and slow response speed under working conditions that require frequent starting and braking.

[0006] Based on this, the present invention optimizes and improves the problems existing in the actual use of the hydraulic winch previously applied for, and hereby proposes a compact hydraulic winch with a large tonnage and high speed ratio to better solve the problems existing in the prior art. Utility Model Content

[0007] The utility model solves one of the above technical problems and adopts the following technical solution: a compact hydraulic winch with large tonnage and high speed ratio, comprising a drum body with a built-in planetary speed change mechanism, the drum body being used for winding a wire rope, a left lateral seat and a right lateral seat being symmetrically installed on the left and right sides of the drum body, the left end of the drum body being movably inserted into a bearing hole installed in the left lateral seat, and the right end of the drum body being movably inserted into a bearing hole installed in the right lateral seat, the bottoms of the left lateral seat and the right lateral seat being fixed to the top of a horizontal mounting seat, a first speed change unit being installed on the right side of the right lateral seat, and a second speed change unit being installed on the left side of the left lateral seat, the output end of the first speed change unit being connected to the input end of the second speed change unit through a linkage member, the output end of the second speed change unit being connected to the planetary speed change mechanism in the drum body, and the input end of the first speed change unit being connected to a large-tonnage hydraulic motor.

[0008] In any of the above schemes, preferably, the first speed change unit includes a first gear box fixedly mounted on the right side wall of the right side stand, and a first transmission gear and a first passive gear are arranged in parallel from top to bottom in the internal mounting cavity of the first gear box, the first transmission gear and the first passive gear are meshed with each other, both ends of the gear shaft of the first transmission gear are movably inserted in the corresponding mounting holes of the first gear box, and both ends of the gear shaft of the first passive gear are movably inserted in the corresponding mounting holes of the first gear box, the right end of the gear shaft of the first transmission gear is movably inserted to the outside of the first gear box and is connected to the output shaft of the hydraulic motor, the hydraulic motor is fixedly mounted on the right side outer wall of the first gear box, and the left end of the gear shaft of the first passive gear is movably inserted to the outside of the first gear box and is connected to the input end of the linkage.

[0009] In any of the above schemes, it is preferred that the linkage member includes a linkage transmission shaft horizontally arranged between the left lateral seat and the right lateral seat, and the two ends of the linkage transmission shaft are respectively fixedly connected to the left end of the gear shaft of the first passive gear and the input end of the second speed change unit through a coupling.

[0010] In any of the above schemes, it is preferred that a steel cylinder sleeve is sleeved on the outer side wall of the linkage transmission shaft, side end covers are respectively installed at both ends of the steel cylinder sleeve, support bearings are respectively installed at both ends of the annular cavity inside the steel cylinder sleeve, each of the support bearings is movably sleeved on the outer side wall of the linkage transmission shaft, and support frames are respectively fixedly installed at the bottom of both ends of the steel cylinder sleeve, and the bottom of each support frame is fixedly installed on the top of the horizontal mounting seat.

[0011] In any of the above schemes, preferably, the second speed change unit includes a second gear box fixedly mounted on the left side wall of the left side stand, and a second driven gear and a second transmission gear are arranged in parallel from top to bottom in the internal mounting cavity of the second gear box, the second driven gear is meshed with the second transmission gear, both ends of the gear shaft of the second transmission gear are movably inserted in the corresponding mounting holes of the second gear box, both ends of the gear shaft of the second driven gear are movably inserted in the corresponding mounting holes of the second gear box, the right end of the gear shaft of the second driven gear is movably inserted to the outside of the second gear box and extends into the reel body and is connected to the planetary speed change mechanism inside it, the right end of the gear shaft of the second transmission gear is movably inserted to the outside of the second gear box and is connected to the linkage transmission shaft through a coupling.

[0012] In any of the above solutions, preferably, annular baffles are integrally formed and fixedly connected to the outer side walls of the left and right ends of the reel body.

[0013] In any of the above schemes, preferably, a reinforcing rib plate is installed on the inner side of each support frame, the bottom of the reinforcing rib plate is fixed to the top of the horizontal base, and one side of the reinforcing rib plate is fixed to the support frame on the corresponding side.

[0014] In any of the above solutions, preferably, the first transmission gear and the first passive gear cooperate to form a reduction gear structure and the transmission ratio thereof is 5:1-3:1.

[0015] In any of the above solutions, preferably, the second transmission gear and the second passive gear cooperate to form a reduction gear structure and the transmission ratio thereof is 4:1-2:1.

[0016] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0017] 1. The compact hydraulic winch with large tonnage and high speed ratio in the utility model has a better speed ratio than the traditional hydraulic winch. It can achieve better speed regulation and deceleration according to the lifting requirements and is effectively applicable to various complex working conditions.

[0018] 2. The hydraulic winch in the present invention adopts a large-tonnage hydraulic motor as the power component when transmitting power, which can better complete the lifting operation of heavy objects during operation; at the same time, it relies on the first speed change unit and the second speed change unit on the left and right sides to change the input power and transmit it to the planetary speed change mechanism of the drum body. The multi-stage speed change can better meet the requirements of operating speed.

[0019] 3. The first and second speed change units rely on linkage parts to achieve power connection and transmission, which can better ensure the stability of the linkage transmission shaft during long-axis transmission and avoid shaft vibration problems caused by excessive transmission distance. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following briefly describes the drawings required for the specific embodiments or the description of the prior art. Similar elements or components are generally identified by similar reference numerals throughout the drawings. Elements or components in the drawings are not necessarily drawn to scale.

[0021] Figure 1 It is a structural diagram of the present utility model.

[0022] Figure 2 This is a schematic diagram of the internal structure of the utility model in a partially cutaway state.

[0023] In the figure, 1. reel body; 2. left lateral stand; 3. right lateral stand; 4. horizontal mounting seat; 5. first speed change unit; 501. first gear box; 502. first transmission gear; 503. first driven gear; 6. second speed change unit; 601. second gear box; 602. second driven gear; 603. second transmission gear; 7. hydraulic motor; 8. linkage transmission shaft; 9. coupling; 10. steel cylinder sleeve; 11. side end cover; 12. annular cavity; 13. support bearing; 14. support frame; 15. annular baffle; 16. reinforcing rib plate. DETAILED DESCRIPTION

[0024] The following embodiments of the present invention are described in detail with reference to the accompanying drawings. The following embodiments are only used to more clearly illustrate the present invention's technical solution and are therefore only examples and are not intended to limit the scope of protection of the present invention. Figure 1-Figure 2 As shown in .

[0025] Example 1: A compact hydraulic winch with large tonnage and high speed ratio, comprising a drum body 1 with a built-in planetary speed change mechanism, the drum body 1 being used for winding a wire rope, and a left lateral stand 2 and a right lateral stand 3 being symmetrically installed on the left and right sides of the drum body 1, respectively, the left end of the drum body 1 being movably inserted into a bearing hole installed in the left lateral stand 2, and the right end of the drum body 1 being movably inserted into a bearing hole installed in the right lateral stand 3, the bottoms of the left lateral stand 2 and the right lateral stand 3 being fixed to the top of a horizontal mounting seat 4, a first speed change unit 5 being installed on the right side of the right lateral stand 3, and a second speed change unit 6 being installed on the left side of the left lateral stand 2, the output end of the first speed change unit 5 being connected to the input end of the second speed change unit 6 through a linkage, the output end of the second speed change unit 6 being connected to the planetary speed change mechanism in the drum body 1, and the input end of the first speed change unit 5 being connected to a large-tonnage hydraulic motor 7.

[0026] It should be noted that the entire hydraulic winch has a higher speed ratio than traditional hydraulic winches, capable of handling more complex lifting and conveying conditions, and has a faster overall speed response. During operation, the hydraulic motor 7 achieves power input at high tonnage, and the transmission of the first speed change unit 5, the linkage, and the second speed change unit 6 controls the speed and torque entering the drum body 1, effectively increasing the operational range of the entire winch.

[0027] When the planetary speed change mechanism receives external input power, it can drive the drum body 1 to operate, thereby realizing the control of the winding of the wire rope wound thereon, ensuring that it can be lifted as needed during subsequent lifting operations.

[0028] In any of the above schemes, it is preferred that the first speed change unit 5 includes a first gear box 501 fixedly mounted on the right side wall of the right side seat 3, and a first transmission gear 502 and a first passive gear 503 are arranged in parallel from top to bottom in the internal mounting cavity of the first gear box 501, the first transmission gear 502 and the first passive gear 503 are meshed with each other, both ends of the gear shaft of the first transmission gear 502 are movably inserted into the corresponding mounting holes of the first gear box 501, and both ends of the gear shaft of the first passive gear 503 are movably inserted into the corresponding mounting holes of the first gear box 501, the right end of the gear shaft of the first transmission gear 502 is movably inserted to the outside of the first gear box 501 and is connected to the output shaft of the hydraulic motor 7, the hydraulic motor 7 is fixedly mounted on the right side outer wall of the first gear box 501, and the left end of the gear shaft of the first passive gear 503 is movably inserted to the outside of the first gear box 501 and is connected to the input end of the linkage.

[0029] It should be noted that: in the first speed change unit 5, the first gear box 501 is fixed as a whole by relying on the angle steel connectors at the upper and lower ends of the first gear box 501. After the first gear box 501 is fixed, power can be input to the first transmission gear 502 through the hydraulic motor 7. The operation of the first transmission gear 502 will drive the first driven gear 503 engaged with it to follow the operation, and finally realize the change of speed. After the speed change, the gear shaft of the first driven gear 503 will drive the linkage part to follow the operation, and finally realize the continued transmission of power and speed to the downstream.

[0030] In any of the above schemes, it is preferred that the linkage member includes a linkage transmission shaft 8 horizontally arranged between the left lateral seat 2 and the right lateral seat 3, and the two ends of the linkage transmission shaft 8 are respectively fixedly connected to the left end of the gear shaft of the first passive gear 503 and the input end of the second speed change unit 6 through a coupling 9.

[0031] It should be noted that the linkage member as a whole uses the linkage transmission shaft 8 as a transmission member, and its two ends are respectively connected to the first speed change unit 5 and the second speed change unit 6, thereby achieving the function of transition connection.

[0032] In any of the above schemes, it is preferred that a steel cylinder sleeve 10 is sleeved on the outer side wall of the linkage transmission shaft 8, and side end covers 11 are respectively installed at both ends of the steel cylinder sleeve 10, and support bearings 13 are respectively installed at both ends of the annular cavity 12 inside the steel cylinder sleeve 10, and each of the support bearings 13 is movably sleeved on the outer side wall of the linkage transmission shaft 8, and support frames 14 are respectively fixedly installed at the bottom of both ends of the steel cylinder sleeve 10, and the bottom of each support frame 14 is fixedly installed on the top of the horizontal mounting seat 4.

[0033] Taking into account that, according to the different length requirements of the reel body 1, the linkage transmission shaft 8 needs to maintain a longer transmission distance, a steel cylinder sleeve 10 is sleeved on its outer wall and the outer wall of the linkage transmission shaft 8 is supported by the support bearings 13 at both ends of the steel cylinder sleeve 10, thereby achieving the purpose of maintaining stable support of the linkage transmission shaft 8 during operation. The support of the bottom support frame 14 can ensure that the shaft vibration problem caused by sagging due to its own weight during operation can be reduced or eliminated, thereby ensuring stability during operation.

[0034] In any of the above schemes, it is preferred that the second speed change unit 6 includes a second gear box 601 fixedly mounted on the left side wall of the left side stand 2, and a second driven gear 602 and a second transmission gear 603 are arranged in parallel from top to bottom in the internal mounting cavity of the second gear box 601, the second driven gear 602 is meshed with the second transmission gear 603, both ends of the gear shaft of the second transmission gear 603 are movably inserted in the corresponding mounting holes of the second gear box 601, and both ends of the gear shaft of the second driven gear 602 are movably inserted in the corresponding mounting holes of the second gear box 601, the right end of the gear shaft of the second driven gear 602 is movably inserted to the outside of the second gear box 601 and extends into the reel body 1 and is connected to the planetary speed change mechanism inside it, and the right end of the gear shaft of the second transmission gear 603 is movably inserted to the outside of the second gear box 601 and is connected to the linkage transmission shaft 8 through the coupling 9.

[0035] It should be noted that: when the second speed change unit 6 is installed, it is bolted to the corresponding left-side stand 2 by relying on the angle steel seats at the upper and lower ends of the second gear box 601. When the linkage inputs power, it will drive the current second driven gear 602 to operate. When the second driven gear 602 is operating, it is engaged with the second transmission gear 603. Therefore, the operation of the second transmission gear 603 will drive the second driven gear 602 to rotate, thereby achieving the purpose of further speed change. After speed change again, the power will be output to the planetary speed change mechanism of the reel body 1 through the gear shaft of the second driven gear 602, thereby driving the entire reel body 1 to operate and realizing high-speed transmission.

[0036] Example 2: This example differs from Example 1 in that it further includes the following technical features:

[0037] In any of the above solutions, preferably, an annular baffle 15 is integrally formed and fixedly connected to the outer side walls of the left and right ends of the reel body 1.

[0038] When the steel wire rope follows the drum body 1 in its operation, the annular baffles 15 on both sides can better serve the purpose of lateral limitation, thereby preventing the steel wire rope from randomly shifting laterally.

[0039] In any of the above schemes, it is preferred that a reinforcing rib 16 is installed on the inner side of each support frame 14, the bottom of the reinforcing rib 16 is fixed to the top of the horizontal base, and one side of the reinforcing rib 16 is fixed to the support frame 14 on the corresponding side.

[0040] The reinforcing ribs 16 designed in the present invention can further reinforce the entire support frame 14 and ensure the stability of the installation of the entire steel cylinder sleeve 10.

[0041] In any of the above solutions, preferably, the first transmission gear 502 cooperates with the first passive gear 503 to form a reduction gear structure, and the transmission ratio thereof is 5:1-3:1.

[0042] In any of the above solutions, preferably, the second transmission gear 603 cooperates with the second passive gear 602 to form a reduction gear structure, and the transmission ratio thereof is 4:1-2:1.

[0043] The first transmission gear 502 and the first passive gear 503 cooperate to form a reduction structure, and the second transmission gear 603 and the second passive gear 602 cooperate to form a reduction structure. The combination of the two can better achieve high-speed ratio transmission, thereby better adapting to complex lifting working conditions.

[0044] The entire hydraulic winch can cope with more complex lifting and conveying conditions, and the overall speed change response is faster.

[0045] When working, the power is turned on and the equipment is started. The hydraulic motor 7 is used to realize the power input under large tonnage. The speed and torque entering the drum body 1 are controlled through the transmission of the first speed change unit 5, the linkage and the second speed change unit 6, effectively improving the operational range of the entire winch operation adjustment.

[0046] When the planetary speed change mechanism receives external input power, it can drive the drum body 1 to operate, thereby realizing the control of the winding of the wire rope wound thereon, ensuring that it can be lifted as needed during subsequent lifting operations.

[0047] From the above, it can be seen that the compact hydraulic winch with large tonnage and high speed ratio has a better speed ratio than the traditional hydraulic winch. It can achieve better speed regulation and deceleration according to the lifting requirements, and is effectively applicable to various complex working conditions; a large-tonnage hydraulic motor 7 is used as a power component during power transmission, which can better complete the lifting operation of heavy objects when working; at the same time, the first speed change unit 5 and the second speed change unit 6 on the left and right sides are used to change the input power and transmit it to the planetary speed change mechanism of the drum body 1, and the multi-stage speed change can better meet the requirements of the operating speed; the first speed change unit 5 and the second speed change unit 6 rely on the linkage parts to realize the connection and transmission of power, which can better ensure the stability of the linkage transmission shaft 8 during the long axis transmission process, and avoid the shaft vibration problem caused by the excessive transmission distance.

[0048] The above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that the technical solutions described in the above embodiments can still be modified, or some or all of the technical features therein can be replaced by equivalents. These modifications or replacements do not deviate the essence of the corresponding technical solutions from the scope of the technical solutions of the embodiments of the present invention. For those skilled in the art, any replacement improvements or changes made to the implementation methods of the present invention fall within the scope of protection of the present invention.

[0049] Anything not described in detail in the present invention is well known to those skilled in the art.

Claims

1. A compact hydraulic winch with a large tonnage and high speed ratio, comprising a drum body with a built-in planetary speed change mechanism, the drum body being used to wind a wire rope, with a left-side stand and a right-side stand symmetrically mounted on the left and right sides of the drum body, respectively, the left end of the drum body being movably inserted into a bearing hole mounted in the left-side stand, and the right end of the drum body being movably inserted into a bearing hole mounted in the right-side stand, characterized in that: The bottoms of the left-side lateral seat and the right-side lateral seat are both fixed on the top of the horizontal mounting seat. A first speed change unit is installed on the right side of the right-side lateral seat, and a second speed change unit is installed on the left side of the left-side lateral seat. The output end of the first speed change unit is connected to the input end of the second speed change unit through a linkage, the output end of the second speed change unit is connected to the planetary speed change mechanism in the reel body, and the input end of the first speed change unit is connected to a large-tonnage hydraulic motor.

2. A compact hydraulic winch with large tonnage and high speed ratio according to claim 1, characterized in that: The first speed change unit includes a first gear box fixedly mounted on the right side wall of the right side stand, and a first transmission gear and a first passive gear are arranged in parallel from top to bottom in the internal mounting cavity of the first gear box, and the first transmission gear and the first passive gear are meshed with each other, and both ends of the gear shaft of the first transmission gear are movably inserted in the corresponding mounting holes of the first gear box, and both ends of the gear shaft of the first passive gear are movably inserted in the corresponding mounting holes of the first gear box, and the right end of the gear shaft of the first transmission gear is movably inserted to the outside of the first gear box and is connected to the output shaft of the hydraulic motor, and the hydraulic motor is fixedly mounted on the right side outer wall of the first gear box, and the left end of the gear shaft of the first passive gear is movably inserted to the outside of the first gear box and is connected to the input end of the linkage.

3. A compact hydraulic winch with large tonnage and high speed ratio according to claim 2, characterized in that: The linkage member includes a linkage transmission shaft horizontally arranged between the left side stand and the right side stand, and both ends of the linkage transmission shaft are respectively fixedly connected to the left end of the gear shaft of the first passive gear and the input end of the second speed change unit through couplings.

4. A compact hydraulic winch with large tonnage and high speed ratio according to claim 3, characterized in that: A steel cylinder sleeve is sleeved on the outer side wall of the linkage transmission shaft, and side end covers are respectively installed at both ends of the steel cylinder sleeve, and support bearings are respectively installed at both ends of the annular cavity inside the steel cylinder sleeve. Each of the support bearings is movably sleeved on the outer side wall of the linkage transmission shaft, and support frames are respectively fixedly installed at the bottom of both ends of the steel cylinder sleeve, and the bottom of each support frame is fixedly installed on the top of the horizontal mounting seat.

5. A compact hydraulic winch with large tonnage and high speed ratio according to claim 4, characterized in that: The second speed change unit includes a second gear box fixedly mounted on the left side wall of the left side stand, and a second driven gear and a second transmission gear are arranged in parallel and spaced from top to bottom in the internal mounting cavity of the second gear box, the second driven gear is meshed with the second transmission gear, and both ends of the gear shaft of the second transmission gear are movably inserted in the corresponding mounting holes of the second gear box, and both ends of the gear shaft of the second driven gear are movably inserted in the corresponding mounting holes of the second gear box, and the right end of the gear shaft of the second driven gear is movably inserted to the outside of the second gear box and extends into the reel body and is connected to the planetary speed change mechanism inside it, and the right end of the gear shaft of the second transmission gear is movably inserted to the outside of the second gear box and is connected to the linkage transmission shaft through a coupling.

6. A compact hydraulic winch with large tonnage and high speed ratio according to claim 5, characterized in that: Annular baffles are integrally formed and fixedly connected to the outer side walls of the left and right ends of the reel body.

7. A compact hydraulic winch with large tonnage and high speed ratio according to claim 6, characterized in that: A reinforcing rib plate is installed on the inner side of each support frame, the bottom of the reinforcing rib plate is fixed to the top of the horizontal base, and one side of the reinforcing rib plate is fixed to the support frame on the corresponding side.

8. The compact hydraulic winch with large tonnage and high speed ratio according to claim 7, characterized in that: The first transmission gear cooperates with the first passive gear to form a reduction gear structure, and the transmission ratio thereof is 5:1-3:

1.

9. A compact hydraulic winch with large tonnage and high speed ratio according to claim 8, characterized in that: The second transmission gear cooperates with the second passive gear to form a reduction gear structure, and the transmission ratio thereof is 4:1-2:1.

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