Synchronous take-up and pay-off device with differential correction function

Abstract

The application provides a synchronous winding and unwinding device with differential correction function, comprising two winding drums, two cable arranging assemblies, and a driving assembly; the driving assembly comprises a driving mechanism, a first transmission mechanism, and a second transmission mechanism; the driving mechanism is in transmission connection with the first transmission mechanism, the first transmission mechanism is in transmission connection with the two winding drums, and is used for driving the two winding drums to rotate synchronously and in the same direction; the second transmission mechanism comprises two distance-adjusting driving structures and two differential speed reduction structures, the driving mechanism is in transmission connection with the two differential speed reduction structures, the two differential speed reduction structures are in transmission connection with the two cable arranging assemblies, and the distance-adjusting driving structure is configured to selectively provide a distance-adjusting driving force to the corresponding differential speed reduction structure; when the distance-adjusting driving structure is in a non-working state, the driving mechanism drives the two cable arranging assemblies to arrange cables through the two differential speed reduction structures; and when the distance-adjusting driving structure is in a working state, the cable arranging assemblies adjust the cable arranging pitch based on the distance-adjusting driving force.

Description

Technical Field

[0001] This application relates to the field of marine oil and gas equipment technology, and in particular to a synchronous deployment and recovery device with differential speed correction function. Background Technology

[0002] When a cable winch simultaneously winds up and winds up two cables (such as umbilical cables), the two cable winders corresponding to the two cables may have inconsistent winding patterns due to installation errors or cumulative errors, resulting in a large deviation in the winding and winding effects of the two cables. Summary of the Invention

[0003] This application provides a synchronous take-up and release device with differential speed correction function to solve the problem of large deviation when two cables are taken up and released at the same time in the known technology.

[0004] This application provides a synchronous take-up and unwinding device with differential speed correction function, including two drums, two cable laying assemblies, and a drive assembly. The two cable laying assemblies are arranged corresponding to the two drums. The drive assembly includes a drive mechanism, a first transmission mechanism, and a second transmission mechanism. The drive mechanism is driven by the first transmission mechanism, and the first transmission mechanism is driven by the two drums to drive the two drums to rotate synchronously and in the same direction. The second transmission mechanism includes two pitch-adjusting drive structures and two differential reduction structures. The drive mechanism is driven by the two differential reduction structures, and the two differential reduction structures are driven by the two cable laying assemblies. The two pitch-adjusting drive structures are arranged corresponding to the two differential reduction structures. The pitch-adjusting drive structure is configured to selectively provide pitch-adjusting drive force to its corresponding differential reduction structure. When the pitch-adjusting drive structure is in a non-working state, the drive mechanism drives the two cable laying assemblies to lay cables through the two differential reduction structures. When the pitch-adjusting drive structure is in a working state, the cable laying assembly adjusts the cable laying pitch based on the pitch-adjusting drive force.

[0005] In one possible implementation, the differential deceleration structure includes: The first sun gear is connected to the drive mechanism. A plurality of first planetary gears are arranged around the first sun gear, and all of the plurality of first planetary gears mesh with the first sun gear; The first planetary carrier is driven to the input end of the cable assembly, and multiple first planetary gears are rotatably connected to the first planetary carrier. A first gear ring, wherein a plurality of first planetary gears are disposed within the first gear ring, and the plurality of first planetary gears mesh with the internal tooth structure of the first gear ring.

[0006] In one possible implementation, the pitch-adjusting drive structure includes a pitch-adjusting drive component and a one-way transmission module. The pitch-adjusting drive component is connected to the first gear ring via the one-way transmission module to drive the first gear ring to rotate and to prevent the first planetary gear from driving the first gear ring to rotate.

[0007] In one possible implementation, the unidirectional transmission module includes a worm gear and a worm wheel structure, the pitch adjustment drive is driven by the worm gear, the worm gear is driven by the worm wheel structure, and the worm wheel structure is integrally formed on the outer peripheral surface of the first gear ring.

[0008] In one possible implementation, the first transmission mechanism includes a first reduction structure and a second reduction structure, and the drive mechanism is drivingly connected to the first reduction structure and the second reduction structure. The first reduction structure is drivingly connected to one of the drums, and the second reduction structure is drivingly connected to the other drum.

[0009] In one possible implementation, the first deceleration structure includes, but is not limited to, a shaft-output planetary deceleration structure, and the second deceleration structure includes, but is not limited to, a shell-output planetary deceleration structure.

[0010] In one possible implementation, the drive mechanism includes: Main drive unit; The main drive shaft has one end connected to the main drive component; The first drive distribution structure has its input end connected to the main drive shaft, and its two first distribution ends are respectively connected to the first reduction structure and the second reduction structure. The second drive distribution structure is disposed at intervals on one side of the first drive distribution structure along the axial direction of the main drive shaft. The input end of the second drive distribution structure is driven to the main drive shaft, and the two second distribution ends of the second drive distribution structure are driven to the two differential reduction structures respectively.

[0011] In one possible implementation, the first drive allocation structure includes: The first bevel gear is coaxially connected to the outer periphery of the main drive shaft; Two second bevel gears are radially disposed on opposite sides of the main drive shaft. Both second bevel gears mesh with the first bevel gear, and the two second bevel gears are coaxially connected to the input end of the first reduction structure and the input end of the second reduction structure, respectively.

[0012] In one possible implementation, the second drive allocation structure includes: The third bevel gear is coaxially connected to the outer periphery of the main drive shaft; Two fourth bevel gears are radially disposed on opposite sides of the main drive shaft. Both fourth bevel gears mesh with the third bevel gear, and both fourth bevel gears are coaxially connected to the input ends of the two differential reduction structures.

[0013] In one possible implementation, the cable laying assembly includes a linear motion mechanism and a cable laying guide wheel. The input end of the linear motion mechanism is throttledly connected to the output end of the differential reduction structure, and the linear motion mechanism is throttledly connected to the cable laying guide wheel to drive the cable laying guide wheel to move along the axis of the drum.

[0014] The synchronous take-up and unwinding device with differential speed correction function of this application drives two drums to rotate through a drive mechanism in conjunction with a first transmission mechanism, and drives two cable laying assemblies to lay cables through a drive mechanism in conjunction with a second transmission mechanism. This allows a single drive mechanism to provide driving force to simultaneously achieve winding rotation and cable laying, thus reducing device cost. Furthermore, the second transmission mechanism uses a differential reduction structure in conjunction with a pitch adjustment drive structure to adjust the cable laying pitch of the cable laying assemblies, thereby ensuring that the cable laying state of both cable laying assemblies remains in a preset state, thus maintaining consistency in the cable laying state of the two cable laying assemblies. Attached Figure Description

[0015] Figure 1 This is a schematic diagram of the structure of the synchronous take-up and take-up device with differential speed correction function in one embodiment of this application.

[0016] Figure 2 This is a schematic diagram of the first transmission mechanism of the synchronous take-up and take-up device with differential correction function in one embodiment of this application.

[0017] Figure 3 This is a schematic diagram of the second transmission mechanism in one embodiment of the synchronous take-up and take-up device with differential correction function of this application.

[0018] Figure 4 for Figure 3 A cross-sectional view of the second transmission mechanism along the IV-IV direction.

[0019] Key component symbols: 100, Synchronous take-up and unwinding device with differential speed correction function; Y, First direction; X, Second direction; 10, Drum; 20, Cable laying assembly; 21, Linear movement mechanism; 22, Cable laying guide wheel; 30, Drive assembly; 31, Drive mechanism; 311, Main drive component; 312, Main drive shaft; 313, First drive distribution structure; 3131, First bevel gear; 3132, Second bevel gear; 314, Second drive distribution structure; 3141, Third bevel gear; 3142, Fourth bevel gear; 32, First transmission mechanism; 321, First reduction structure; 3211, First reduction housing; 3212, Second sun gear; 3213, Second planetary gear; 3214, Second planetary carrier; 3215, Second gear ring; 3216, Third sun gear; 321 7. Third planetary gear; 3218. Third planetary carrier; 3219. Third ring gear; 322. Second reduction structure; 3221. Second reduction housing; 3222. Fourth sun gear; 3223. Fourth planetary gear; 3224. Fourth ring gear; 3225. Fifth sun gear; 3226. Fifth planetary gear; 3227. Fourth planetary carrier; 3228. Fifth planetary carrier; 33. Second transmission mechanism; 331. Differential reduction structure; 3311. Differential reduction gearbox; 3312. First sun gear; 3313. First planetary gear; 3314. First planetary carrier; 3315. First ring gear; 33150. Internal gear structure; 332. Adjustable pitch drive structure; 3321. Adjustable pitch drive component; 3322. One-way transmission module; 33221. Worm gear; 33222. Worm wheel structure.

[0020] The following detailed description, in conjunction with the accompanying drawings, will further illustrate this application. Detailed Implementation

[0021] The following description will refer to the accompanying drawings to provide a more complete picture of the present application. The drawings illustrate exemplary embodiments of the present application. However, the present application may be implemented in many different forms and should not be construed as limited to the exemplary embodiments set forth herein. These exemplary embodiments are provided to make the present application thorough and complete, and to fully convey the scope of the present application to those skilled in the art. The same reference numerals denote the same or similar components.

[0022] The terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to limit the application. As used herein, unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “the” are intended to also include the plural forms. Furthermore, when used herein, “comprising” and / or “including” and / or “having,” integers, steps, operations, components, and / or components, but does not exclude the presence or addition of one or more other features, regions, integers, steps, operations, components, and / or groups thereof.

[0023] Unless otherwise defined, all terms used herein (including technical and scientific terms) have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains. Furthermore, unless expressly defined herein, terms such as those defined in a general dictionary should be interpreted as having the same meaning as they have in the relevant art and in the content of this application, and will not be interpreted as having an idealized or overly formal meaning.

[0024] The specific embodiments of this application will be further described in detail below with reference to the accompanying drawings.

[0025] like Figures 1 to 3 As shown, this embodiment provides a synchronous take-up and unwinding device 100 with differential speed correction function, including two drums 10, two cable laying assemblies 20, and a drive assembly 30.

[0026] Two cable laying assemblies 20 are configured corresponding to two drums 10 to lay cables wound on the two drums 10 respectively. The drive assembly 30 includes a drive mechanism 31, a first transmission mechanism 32, and a second transmission mechanism 33. The drive mechanism 31 is driveably connected to the first transmission mechanism 32, and the first transmission mechanism 32 is driveably connected to the two drums 10, driving the two drums 10 to rotate synchronously and in the same direction. The second transmission mechanism 33 includes two pitch-adjusting drive structures 332 and two differential reduction structures 331. The drive mechanism 31 is driveably connected to the two differential reduction structures 331, and the two differential reduction structures 331 are drively connected to the two cable laying assemblies 20. The two pitch-adjusting drive structures 332 are correspondingly configured to selectively provide pitch-adjusting drive force to their corresponding differential reduction structures 331. When the pitch-adjusting drive structure 332 is not in operation, the drive mechanism 31 drives the two cable-laying assemblies 20 to lay cables through the two differential reduction structures 331. When the pitch-adjusting drive structure 332 is in operation, the cable-laying assemblies 20 adjust the cable-laying pitch based on the pitch-adjusting drive force.

[0027] Thus, the synchronous take-up and unwinding device 100 with differential speed correction function of this application drives two drums 10 to rotate through the drive mechanism 31 in conjunction with the first transmission mechanism 32, and drives two cable laying assemblies 20 to lay cables through the drive mechanism 31 in conjunction with the second transmission mechanism 33. This allows a single drive mechanism 31 to provide driving force to simultaneously achieve winding rotation and cable laying of the cable laying assemblies 20, thereby reducing device costs. In addition, the second transmission mechanism 33 uses a differential reduction structure 331 in conjunction with a pitch adjustment drive structure 332 to adjust the cable laying pitch of the cable laying assemblies 20, thereby ensuring that the cable laying state of the two cable laying assemblies 20 is maintained in a preset state, thus ensuring that the cable laying state of the two cable laying assemblies 20 is consistent.

[0028] Please combine Figure 1 and Figure 2In one embodiment, the first transmission mechanism 32 includes a first reduction structure 321 and a second reduction structure 322. The drive mechanism 31 is connected to the first reduction structure 321 and the second reduction structure 322. The first reduction structure 321 is connected to one drum 10, and the second reduction structure 322 is connected to the other drum 10. Thus, the first reduction structure 321 and the second reduction structure 322 reduce the speed and increase the torque of the driving force provided by the drive mechanism 31 to the two drums 10, thereby ensuring the stability of the rotation of the two drums 10.

[0029] In this embodiment, the drive mechanism 31 includes a main drive member 311, a main drive shaft 312, a first drive distribution structure 313, and a second drive distribution structure 314.

[0030] The axis of the main drive shaft 312 is defined as the first direction Y, and the radial direction of the main drive shaft 312 is defined as the second direction X, which is perpendicular to the first direction Y. Along the second direction X, two drums 10 are respectively positioned on opposite sides of the main drive shaft 312. The main drive component 311 can be a pneumatic motor drive device. One end of the main drive shaft 312 is connected to the main drive component 311, for example, one end of the main drive shaft 312 is coaxially connected to the output end of the main drive component 311 via a coupling, so that the main drive shaft 312 is driven to rotate by the main drive component 311. It is understood that in other embodiments, the main drive component 311 can also be a motor or hydraulic motor, etc.

[0031] The input end of the first drive distribution structure 313 is connected to the main drive shaft 312. The two first distribution ends of the first drive distribution structure 313 are respectively connected to the first reduction structure 321 and the second reduction structure 322, so that when the main drive shaft 312 rotates, the first drive distribution structure 313 can provide driving force to the first reduction structure 321 and the second reduction structure 322.

[0032] Along the first direction Y, the second drive distribution structure 314 is spaced apart on the side of the first drive distribution structure 313 away from the main drive member 311. The input end of the second drive distribution structure 314 is connected to the main drive shaft 312. The two second distribution ends of the second drive distribution structure 314 are respectively connected to two differential reduction structures 331, so that when the main drive shaft 312 rotates, the second drive distribution structure 314 can provide driving force to the two differential reduction structures 331.

[0033] Please combine Figure 1 and Figure 2In one embodiment, the first drive distribution structure 313 includes a first bevel gear 3131 and two second bevel gears 3132. The first bevel gear 3131 is coaxially connected to the outer periphery of the main drive shaft 312. The two second bevel gears 3132 are radially disposed on opposite sides of the main drive shaft 312, and both second bevel gears 3132 mesh with the first bevel gear 3131. The two second bevel gears 3132 are coaxially connected to the input ends of the first reduction structure 321 and the second reduction structure 322, respectively.

[0034] The axis of the first bevel gear 3131 is parallel to the first direction Y, and the axes of the two second bevel gears 3132 are parallel to the second direction X. Along the second direction X, the two second bevel gears 3132 are located on opposite sides of the first bevel gear 3131, and the first bevel gear 3131 meshes with the two second bevel gears 3132 to drive the first bevel gear 3131 to rotate synchronously through the main drive shaft 312, and then drive the two second bevel gears 3132 to rotate synchronously through the first bevel gear 3131, so as to provide driving force to the first reduction structure 321 and the second reduction structure 322 simultaneously.

[0035] In this embodiment, the first bevel gear 3131 and the two second bevel gears 3132 each have 20 teeth.

[0036] Furthermore, the first reduction structure 321 includes, but is not limited to, a planetary reduction structure with shaft output, and the second reduction structure 322 includes, but is not limited to, a planetary reduction structure with shell output. The output directions of the first reduction structure 321 and the second reduction structure 322 are opposite, so that when the rotation directions of the two second bevel gears 3132 are opposite, the two drums 10 can rotate synchronously and in the same direction, that is, the cable winding and unwinding directions of the two drums 10 are consistent.

[0037] In this embodiment, the first reduction structure 321 employs two sets of planetary gears to increase the reduction ratio. The first reduction structure 321 includes a first reduction housing 3211, a second sun gear 3212, multiple second planetary gears 3213, a second planetary carrier 3214, a second ring gear 3215, a third sun gear 3216, multiple third planetary gears 3217, a third planetary carrier 3218, and a third ring gear 3219.

[0038] The axis of the second sun gear 3212 is parallel to the second direction X, and the second sun gear 3212 can be coaxially connected to a second bevel gear 3132 via a shaft. Multiple second planet gears 3213 are located within the second gear ring 3215, which is fixedly connected to the first reduction housing 3211. There are three second planet gears 3213. The three second planet gears 3213 are arranged around the second sun gear 3212, and are spaced 120° apart. The side of each second planet gear 3213 closest to the second sun gear 3212 meshes with the second sun gear 3212, while the side of each second planet gear 3213 furthest from the second sun gear 3212 meshes with the internal teeth of the second gear ring 3215. All three second planet gears 3213 are rotatably connected to the second planet carrier 3214.

[0039] The third sun gear 3216 is coaxially arranged with the second sun gear 3212 along the second direction X. The third sun gear 3216 is spaced apart on the side of the second sun gear 3212 away from the second bevel gear 3132, and the third sun gear 3216 can be coaxially connected to the second planetary carrier 3214 via a shaft. Multiple third planetary gears 3217 are located within the third gear ring 3219, which is fixedly connected to the second gear ring 3215. There are three third planetary gears 3217. The three third planetary gears 3217 are arranged around the third sun gear 3216, and are spaced 120° apart. The side of the three third planetary gears 3217 closest to the third sun gear 3216 meshes with the third sun gear 3216, and the side of the three third planetary gears 3217 away from the third sun gear 3216 meshes with the internal teeth of the third gear ring 3219. All three third planetary gears 3217 are rotatably connected to the third planetary carrier 3218, and the third planetary carrier 3218 is coaxially connected to a drum 10 via a shaft.

[0040] Thus, when the second bevel gear 3132 drives the second sun gear 3212, which is coaxially connected to it, to rotate, the second sun gear 3212 drives the three second planet gears 3213 to rotate. The three second planet gears 3213 roll along the internal teeth of the second gear ring 3215, thereby driving the second planet carrier 3214 to rotate. The second planet carrier 3214 then drives the third sun gear 3216 to rotate. The third sun gear 3216 drives the three third planet gears 3217 to rotate. The three third planet gears 3217 roll along the internal teeth of the third gear ring 3219, thereby driving the third planet carrier 3218 to rotate. The third planet carrier 3218 then drives the drum 10, which is coaxially connected to it, to rotate.

[0041] In this embodiment, the second sun gear 3212 has 28 teeth, the second planet gear 3213 has 24 teeth, the second ring gear 3215 has 77 internal teeth, the third sun gear 3216 has 24 teeth, the third planet gear 3217 has 24 teeth, and the third ring gear 3219 has 72 internal teeth. The reduction ratio of the first reduction structure 321 is (72 / 24+1)×(77 / 28+1)=15, and the input and output directions are the same.

[0042] In this embodiment, the second reduction structure 322 employs two sets of planetary gears to increase the reduction ratio. The second reduction structure 322 includes a second reduction housing 3221, a fourth sun gear 3222, multiple fourth planetary gears 3223, a fourth planetary carrier 3227, a fifth sun gear 3225, multiple fifth planetary gears 3226, a fifth planetary carrier 3228, and a fourth ring gear 3224. The fourth sun gear 3222, multiple fourth planetary gears 3223, fourth planetary carrier 3227, fifth sun gear 3225, multiple fifth planetary gears 3226, and fifth planetary carrier 3228 are all located within the fourth ring gear 3224.

[0043] The axis of the fourth sun gear 3222 is parallel to the second direction X, and the fourth sun gear 3222 can be coaxially connected to another second bevel gear 3132 via a shaft. There are three fourth planet gears 3223. The three fourth planet gears 3223 are arranged around the fourth sun gear 3222, and are spaced 120° apart. The side of each of the three fourth planet gears 3223 closest to the fourth sun gear 3222 meshes with the fourth sun gear 3222, and the side of each of the three fourth planet gears 3223 furthest from the fourth sun gear 3222 meshes with the internal teeth of the fourth ring gear 3224. All three fourth planet gears 3223 are rotatably connected to the fourth planet carrier 3227.

[0044] The fifth sun gear 3225 is coaxially arranged with the fourth sun gear 3222 along the second direction X, and is spaced apart from the fourth sun gear 3222 on the side away from the second bevel gear 3132. There are three fifth planet gears 3226. The three fifth planet gears 3226 are arranged around the fifth sun gear 3225, and are spaced 120° apart. The sides of the three fifth planet gears 3226 closest to the fifth sun gear 3225 mesh with the fifth sun gear 3225, and the sides of the three fifth planet gears 3226 away from the fifth sun gear 3225 mesh with the internal teeth of the fourth ring gear 3224. All three fifth planet gears 3226 are rotatably connected to the fifth planet carrier 3228.

[0045] The fourth planetary carrier 3227 is fixedly connected to the second reduction housing 3221. The fifth planetary carrier 3228 is integrally formed or fixedly connected to the fourth gear ring 3224. The fourth gear ring 3224 is rotatably connected to the second reduction housing 3221 so that the fourth gear ring 3224 can rotate relative to the second reduction housing 3221. The fourth gear ring 3224 is coaxially connected to another drum 10 so as to drive the connected drum 10 to rotate through the fourth gear ring 3224.

[0046] Thus, when the second bevel gear 3132 drives the fourth sun gear 3222, which is coaxially connected to it, to rotate, the fourth sun gear 3222 drives the three fourth planet gears 3223 to rotate, the three fourth planet gears 3223 drive the fourth ring gear 3224 to rotate, and the rotation of the fourth ring gear 3224 will drive the three fifth planet gears 3226 to rotate. As a result, the rotation of the fourth ring gear 3224 is driven by the fourth planet gears 3223 and the fifth planet gears 3226, which in turn provide driving force to the drum 10 and drive the drum 10 to rotate.

[0047] In this embodiment, the fourth sun gear 3222 has 20 teeth, the fourth planet gear 3223 has 20 teeth, the fifth sun gear 3225 has 20 teeth, the fifth planet gear 3226 has 20 teeth, and the internal teeth of the fourth gear ring 3224 have 60 teeth. The reduction ratio of the second reduction structure 322 is (60 / 20+1)×(60 / 20+1)-1=15, and the input and output directions are opposite.

[0048] Please combine Figure 3 and Figure 4 In one embodiment, the second drive distribution structure 314 includes a third bevel gear 3141 and two fourth bevel gears 3142, which are arranged radially on opposite sides of the main drive shaft 312.

[0049] The axis of the third bevel gear 3141 is parallel to the first direction Y and along the first direction Y. The third bevel gear 3141 is spaced apart on the side of the first bevel gear 3131 away from the main drive member 311. The third bevel gear 3141 is coaxially connected to the outer periphery of the main drive shaft 312 so as to drive the third bevel gear 3141 to rotate through the main drive shaft 312.

[0050] Along the second direction X, two fourth bevel gears 3142 are respectively disposed on opposite sides of the third bevel gear 3141. The axes of the two fourth bevel gears 3142 are parallel to the second direction X. Both fourth bevel gears 3142 mesh with the third bevel gear 3141, and the two fourth bevel gears 3142 are coaxially connected to the input ends of the two differential reduction structures 331, so that the third bevel gear 3141 drives the two fourth bevel gears 3142 to rotate, and then drives the differential reduction structures 331 connected to them to work.

[0051] In this embodiment, the third bevel gear 3141 has 20 teeth, and the two fourth bevel gears 3142 each have 50 teeth.

[0052] Please combine Figures 3 to 4 And see Figure 1 In one embodiment, the differential reduction structure 331 includes a differential reduction gearbox 3311, a first sun gear 3312, a plurality of first planet gears 3313, a first planet carrier 3314, and a first ring gear 3315. The first sun gear 3312 is driven to the drive mechanism 31. The plurality of first planet gears 3313 are arranged around the first sun gear 3312, and all of the plurality of first planet gears 3313 mesh with the first sun gear 3312. The first planet carrier 3314 is driven to the input end of the cable assembly 20, and all of the plurality of first planet gears 3313 are rotatably connected to the first planet carrier 3314. The plurality of first planet gears 3313 are disposed within the first ring gear 3315, and all of the plurality of first planet gears 3313 mesh with the internal tooth structure 33150 of the first ring gear 3315.

[0053] Along the second direction X, the differential gearbox 3311 is spaced apart on the side of its corresponding fourth bevel gear 3142 away from the other fourth bevel gear 3142. The first sun gear 3312, a plurality of first planet gears 3313, the first planet carrier 3314, and the first ring gear 3315 are all located inside the differential gearbox 3311.

[0054] The axis of the first sun gear 3312 is parallel to the second direction X, and the first sun gear 3312 is coaxially connected to a fourth bevel gear 3142 through a shaft, so as to drive the first sun gear 3312 connected thereto to rotate through the fourth bevel gear 3142.

[0055] The axis of the first planetary gear 3313 is parallel to the second direction X. There are three first planetary gears 3313, which are evenly distributed around the outer circumference of the first sun gear 3312, with a 120° interval between any two adjacent first planetary gears 3313. The first planetary carrier 3314 is rotatably connected to the differential gearbox 3311, and all three first planetary gears 3313 are rotatably connected to the first planetary carrier 3314. The first planetary carrier 3314 is coaxially connected to the input end of the cable assembly 20 to provide driving force to the cable assembly 20.

[0056] The axis of the first gear ring 3315 is parallel to the second direction X, and the first gear ring 3315 is rotatably connected to the differential gearbox 3311. All three first planetary gears 3313 are located within the first gear ring 3315, with the side of the three first planetary gears 3313 closest to the first sun gear 3312 meshing with the first sun gear 3312, and the side of the three first planetary gears 3313 furthest from the first sun gear 3312 meshing with the internal gear structure 33150 of the first gear ring 3315.

[0057] In this embodiment, the pitch adjustment drive structure 332 includes a pitch adjustment drive component 3321 and a one-way transmission module 3322. The pitch adjustment drive component 3321 is connected to the first gear ring 3315 through the one-way transmission module 3322, and is used to drive the first gear ring 3315 to rotate, and prevent the first planetary gear 3313 from driving the first gear ring 3315 to rotate.

[0058] The unidirectional transmission module 3322 includes a worm gear 33221 and a worm wheel structure 33222. The pitch-adjusting drive component 3321 is connected to the worm gear 33221, and the worm gear 33221 is connected to the worm wheel structure 33222. The worm wheel structure 33222 is integrally formed on the outer circumferential surface of the first gear ring 3315, meaning the worm wheel structure 33222 can serve as an external tooth structure on the outer circumferential surface of the first gear ring 3315. The worm gear 33221 is rotatably connected to the differential gearbox 3311, and the axis of the worm gear 33221 is perpendicular to the axis of the first gear ring 3315. The pitch-adjusting drive component 3321 is a drive device such as a pneumatic motor. The pitch-adjusting drive component 3321 is located outside the differential gearbox 3311 and is connected to the worm gear 33221 to drive its rotation. The worm 33221 meshes with the worm wheel structure 33222 to drive the worm wheel structure 33222 to rotate, thereby enabling the worm 33221 to drive the first gear ring 3315 to rotate. However, the worm 33221 and the worm wheel have a self-locking capability. When the worm 33221 is in a non-rotating state, the first gear ring 3315 is restricted by the worm 33221 and cannot rotate.

[0059] Thus, when the cable laying assembly 20 is working normally and does not require adjustment, the first sun gear 3312 drives the three first planetary gears 3313 to rotate, the first gear ring 3315 is limited by the worm gear 33221 and is in a fixed state, the three first planetary gears 3313 roll along the internal tooth structure 33150 of the first gear ring 3315, thereby driving the first planetary carrier 3314 to rotate through the three first planetary gears 3313, and then providing the cable laying assembly 20 with the driving force for cable laying operation through the first planetary carrier 3314. The first sun gear 3312, the first planetary gears 3313, and the first gear ring 3315 constitute the cable laying deceleration structure, and the degree of freedom of the cable laying deceleration structure is 1.

[0060] When the cable laying assembly 20 needs to be adjusted, the pitch adjustment drive 3321 drives the first gear ring 3315 to rotate, the first gear ring 3315 drives the three first planetary gears 3313 to rotate around the first sun gear 3312, the three first planetary gears 3313 in turn drive the first planetary carrier 3314 to rotate, and then the first planetary carrier 3314 provides a driving force for adjusting the cable laying pitch of the cable laying assembly 20, thereby adjusting the cable laying assembly 20 to the normal state.

[0061] In this embodiment, the first sun gear 3312 has 17 teeth, the first planet gear 3313 has 34 teeth, the internal gear structure 33150 of the first gear ring 3315 has 85 teeth, and the worm gear structure 33222 has 135 teeth. The reduction ratio of the cable reduction structure is 85 / 17+1=6.

[0062] When the pitch adjustment drive 3321 is working, the second transmission mechanism 33 has 2 degrees of freedom. The ratio of the input shaft speed to the output shaft speed of the second transmission mechanism 33 will no longer be 6. Its output speed will be related to the input speed of the pitch adjustment drive 3321. When the pitch adjustment drive 3321 rotates forward or backward, the output shaft speed of the second transmission mechanism 33 can also be adjusted in the forward or reverse direction. That is, when the pitch adjustment drive 3321 rotates 135 revolutions, the output shaft of the bevel gear distributor composed of the third bevel gear 3141 and the two fourth bevel gears 3142 can rotate 1 revolution forward or backward respectively based on the original position. When the cable is transmitted to the cable laying assembly 20, the cable laying pitch of the cable laying assembly 20 can be adjusted independently.

[0063] Furthermore, the cable laying assembly 20 includes a linear motion mechanism 21 and a cable laying guide wheel 22. The input end of the linear motion mechanism 21 is driven to the output end of the differential reduction structure 331, and the linear motion mechanism 21 is driven to the cable laying guide wheel 22 to drive the cable laying guide wheel 22 to move along the direction of the axis of the drum 10.

[0064] The linear motion mechanism 21 is a lead screw and slide mechanism. The axis of the lead screw in the lead screw and slide mechanism is parallel to the second direction X, and one end of the lead screw is coaxially connected to the first planetary carrier 3314 to drive the lead screw to rotate. The cable guide wheel 22 is connected to the lead screw nut slide of the lead screw and slide mechanism. When the lead screw rotates, the lead screw drives the lead screw nut slide to slide relative to the lead screw along the second direction X, thereby realizing the sliding of the cable guide wheel 22 along the second direction X to adjust the axial position of the cable guide wheel 22 relative to the lead screw.

[0065] In this embodiment, as mentioned above, the third bevel gear 3141 has 20 teeth, and the two fourth bevel gears 3142 each have 50 teeth. The reduction ratio of the entire mechanism, consisting of the bevel gear distributor formed by the third bevel gear 3141 and the two fourth bevel gears 3142, and the second transmission mechanism 33, is (50 / 20) × (85 / 17 + 1) = 15, which is the same as the reduction ratio of the first reduction structure 321 and the second reduction structure 322 mentioned above. Furthermore, the pitch of the lead screws in both cable laying assemblies 20 is 82. Thus, when the drum 10 rotates one revolution, the lead screw also rotates one revolution, and the cable laying guide wheel 22 can move 82mm along the second direction X, meeting the cable laying requirement of an umbilical cable diameter of 80mm.

[0066] It is understood that in other embodiments, parameters such as the lead screw pitch or the reduction ratio of each reduction mechanism and transmission mechanism can be adjusted according to the umbilical cable of different diameters.

[0067] In summary, this application employs a combination of bevel gears and planetary gears to achieve multiple outputs from a single input. Because this application uses mechanical transmission with a fixed gear ratio, it facilitates achieving preset effects and allows for fine-tuning of each of the two cable-laying assemblies 20. Furthermore, the two drums 10 of this application utilize synchronous mechanical transmission, achieving high synchronization accuracy. The drive mechanism 31 is centrally located, distributing the output to both sides, resulting in a compact axial dimension and a centrally located center of gravity, ensuring stable lifting and avoiding uneven loading of the slings, which is detrimental to marine lifting and transportation requirements. Additionally, all transmission devices in this application employ a closed gearbox structure, providing high levels of corrosion and explosion resistance.

[0068] The specific embodiments of this application have been described above with reference to the accompanying drawings. However, those skilled in the art will understand that various changes and substitutions can be made to the specific embodiments of this application without departing from the scope of this application. All such changes and substitutions fall within the scope defined by this application.

Claims

1. A synchronous take-up and release device with differential speed correction function, characterized in that, include: Two rolls; Two cable routing assemblies are provided, corresponding to the two aforementioned drums; A drive assembly, comprising a drive mechanism, a first transmission mechanism, and a second transmission mechanism; The drive mechanism is connected to the first transmission mechanism, and the first transmission mechanism is connected to the two drums to drive the two drums to rotate synchronously and in the same direction. The second transmission mechanism includes two pitch-adjusting drive structures and two differential reduction structures. The drive mechanism is driven by the two differential reduction structures, and the two differential reduction structures are driven by the two cable-laying assemblies. The two pitch-adjusting drive structures are correspondingly arranged with the two differential reduction structures. The pitch-adjusting drive structure is configured to selectively provide pitch-adjusting drive force to its corresponding differential reduction structure. The differential reduction structure includes a first sun gear, a plurality of first planet gears, a first planet carrier, and a first ring gear. The first sun gear is driven by the drive mechanism. A plurality of first planetary gears are arranged around the first sun gear, and all of the plurality of first planetary gears mesh with the first sun gear; a first planetary carrier is driven to the input end of the cable assembly, and the plurality of first planetary gears are rotatably connected to the first planetary carrier; the plurality of first planetary gears are disposed within the first gear ring, and all of the plurality of first planetary gears mesh with the internal tooth structure of the first gear ring; the pitch adjustment drive structure includes a pitch adjustment drive component and a one-way transmission module, the pitch adjustment drive component is driven to the first gear ring through the one-way transmission module, and is used to drive the first gear ring to rotate, and prevent the first planetary gears from driving the first gear ring to rotate; When the pitch adjustment drive structure is in a non-working state, the drive mechanism drives the two cable laying assemblies to lay cables through the two differential reduction structures; when the pitch adjustment drive structure is in a working state, the cable laying assemblies adjust the cable laying pitch based on the pitch adjustment drive force.

2. The synchronous take-up and release device with differential speed correction function as described in claim 1, characterized in that, The unidirectional transmission module includes a worm gear and a worm wheel structure. The pitch adjustment drive is connected to the worm gear, and the worm gear is connected to the worm wheel structure. The worm wheel structure is integrally formed on the outer peripheral surface of the first gear ring.

3. The synchronous take-up and release device with differential speed correction function as described in claim 1, characterized in that, The first transmission mechanism includes a first reduction structure and a second reduction structure. The drive mechanism is driven to connect the first reduction structure and the second reduction structure. The first reduction structure is driven to connect one of the drums, and the second reduction structure is driven to connect the other drum.

4. The synchronous take-up and release device with differential speed correction function as described in claim 3, characterized in that, The first reduction structure includes, but is not limited to, a planetary reduction structure with shaft output, and the second reduction structure includes, but is not limited to, a planetary reduction structure with shell output.

5. The synchronous take-up and release device with differential speed correction function as described in claim 3, characterized in that, The drive mechanism includes: Main drive unit; The main drive shaft has one end connected to the main drive component; The first drive distribution structure has its input end connected to the main drive shaft, and its two first distribution ends are respectively connected to the first reduction structure and the second reduction structure. The second drive distribution structure is disposed at intervals on one side of the first drive distribution structure along the axial direction of the main drive shaft. The input end of the second drive distribution structure is driven to the main drive shaft, and the two second distribution ends of the second drive distribution structure are driven to the two differential reduction structures respectively.

6. The synchronous take-up and release device with differential speed correction function as described in claim 5, characterized in that, The first driver allocation structure includes: The first bevel gear is coaxially connected to the outer periphery of the main drive shaft; Two second bevel gears are radially disposed on opposite sides of the main drive shaft. Both second bevel gears mesh with the first bevel gear, and the two second bevel gears are coaxially connected to the input end of the first reduction structure and the input end of the second reduction structure, respectively.

7. The synchronous take-up and release device with differential speed correction function as described in claim 5, characterized in that, The second drive allocation structure includes: The third bevel gear is coaxially connected to the outer periphery of the main drive shaft; Two fourth bevel gears are radially disposed on opposite sides of the main drive shaft. Both fourth bevel gears mesh with the third bevel gear, and both fourth bevel gears are coaxially connected to the input ends of the two differential reduction structures.

8. The synchronous take-up and release device with differential speed correction function as described in claim 1, characterized in that, The cable laying assembly includes a linear motion mechanism and a cable laying guide wheel. The input end of the linear motion mechanism is driven to the output end of the differential reduction structure, and the linear motion mechanism is driven to the cable laying guide wheel to drive the cable laying guide wheel to move along the axis of the drum.

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