A marine dual-gas-turbine power branch transmission mechanism and operation mode switching method

Abstract

A marine dual gas turbine power branch transmission mechanism and operating mode switching method are disclosed. The transmission mechanism includes a shaft assembly, a front gear assembly, a middle gear assembly, and a rear gear assembly. A large front gear is mounted on the fifth and seventh shafts respectively. A small front gear mounted on the first shaft meshes with two large front gears. A large front gear mounted on the seventh shaft meshes with a transverse gear mounted on the eighth shaft. The eighth shaft is connected to the transverse gear end via a friction clutch. The input end of the front gas turbine is connected to the first shaft via a first synchronous automatic clutch. A small rear gear mounted on the second shaft meshes with two large rear gears. The input end of the rear gas turbine is connected to the second shaft via a second synchronous automatic clutch. The output gear meshes with two first and two second small and middle gears respectively. This invention features a compact structure, strong power transmission capability, stable ship operation during switching, and adaptability to various operating conditions.

Description

Technical Field

[0001] This invention relates to a power transmission structure and operation switching control method for marine gas turbines, specifically to a power branch transmission mechanism for dual marine gas turbines and a method for switching operating modes, belonging to the field of marine power propulsion transmission. Background Technology

[0002] Large marine propulsion systems require gear transmission structures capable of simultaneously transmitting power from two high-power gas turbines, while also transferring power to the other side or vice versa. Due to the numerous operating conditions of the transmission structure, smooth switching under varying conditions is impossible, and there are issues such as excessively large and heavy gearboxes, leading to larger ship sizes and lower speeds.

[0003] CN115031979A relates to a small-scale semi-physical simulation test bench for a combined gas turbine and gas turbine propulsion system. By incorporating a variable frequency motor, a servo control system, a three-axis gearbox, a five-axis gearbox, and an eddy current dynamometer, the test bench establishes an operating principle consistent with that of an actual ship's multi-engine system, capable of simulating various ship operating states. However, using a variable frequency motor to simulate a gas turbine and an eddy current dynamometer to simulate a marine propeller constitutes a semi-physical simulation test bench, which cannot achieve parallel operation of two gas turbines using a single structure, thus failing to meet practical needs.

[0004] CN113551915A relates to a semi-physical simulation test bench and test method for a combined diesel and gas turbine (DGT) multi-engine parallel operation device. It features a wide power coverage range, including a high-speed electric motor, a medium-speed electric motor, a hydraulic dynamometer, and an electric turbine dynamometer, capable of meeting the power requirements of ships under all operating conditions. Primarily used for semi-physical simulation research, it employs different components as the prime mover for different operating conditions. For example, under low operating conditions, a diesel engine can be used as the prime mover for high efficiency; under medium operating conditions, a gas turbine can be used; and under high operating conditions, a combined diesel and gas turbine power output can be used. At full operating conditions, a dual-diesel / dual-gas turbine power output is used. However, this document requires different prime movers to switch modes under different operating conditions, which is cumbersome and prevents the use of a single structure to achieve parallel operation of two types of gas turbines. Summary of the Invention

[0005] To overcome the limitations of existing technologies, this invention provides a power branch transmission mechanism for marine dual gas turbines and a method for switching operating modes.

[0006] A marine dual gas turbine power branch transmission mechanism includes a shaft assembly, a front gear assembly, a middle gear assembly, and a rear gear assembly; the shaft assembly includes a first shaft, a second shaft, a third shaft, a fourth shaft, a fifth shaft, a sixth shaft, a seventh shaft, and an eighth shaft; The front gear assembly includes a front pinion, a transverse gear, and two front large gears; one front large gear is mounted on each of the fifth and seventh shafts; the front pinion mounted on the first shaft meshes with the two front large gears; the front large gear mounted on the seventh shaft meshes with the transverse gear mounted on the eighth shaft; the eighth shaft is connected to the transverse gear end via a friction clutch. The input end of the gas turbine is connected to the first shaft via a first synchronous automatic clutch; The intermediate gear assembly includes two first small gears and two second small gears, and the rear gear assembly includes a rear small gear and two rear large gears; one first small gear is installed on the fifth shaft and one seventh shaft respectively, one second small gear and one rear large gear are installed on the fourth shaft, and one second small gear and one rear large gear are installed on the sixth shaft respectively. The rear small gear installed on the second shaft meshes with the two rear large gears respectively, and the input end of the rear gas turbine is connected to the second shaft through a second synchronous automatic clutch; An output gear is mounted on the third shaft at the load output end, and the output gear meshes with two first pinion gears and two second pinion gears respectively.

[0007] Furthermore, the transmission mechanism includes four operating modes: dual gas turbine parallel operation single output mode, single gas turbine input single output mode, single gas turbine input dual output mode, and single gas turbine and transverse gear parallel operation input single output mode.

[0008] The advantages of this invention compared to the prior art are: 1. The present invention provides a forward gas turbine, a transmission mechanism, and a rear gas turbine arranged sequentially from bow to stern, with the transmission mechanism located on one side of the ship. This allows the ship to select different gas turbines for operation under different working conditions. It also has the ability to transmit power from the transmission device of the present invention to the other side of the ship or from the other side of the ship to the transmission mechanism of the present invention, thereby making the power matching of the ship more reasonable.

[0009] 2. The present invention designs a three-layer gear assembly with a compact overall structure, which enhances the power transmission capability of the power branch transmission mechanism and solves the problems of excessively large overall size and weight of the gearbox, resulting in larger and heavier ships and lower speeds.

[0010] 3. The power branch transmission mechanism of the present invention has multiple operating modes, such as dual gas turbine parallel single output mode, single gas turbine input single output mode, single gas turbine input dual output mode, and single gas turbine and transverse gear parallel input single output mode, forming multiple switching control strategies. Under the condition of ensuring constant ship speed, a set of power branch transmission mechanisms can achieve smooth and seamless switching of operating conditions, ensure stable ship operation, and adapt to various operating conditions.

[0011] The technical solution of the present invention will be further described below with reference to the accompanying drawings and embodiments: Attached Figure Description

[0012] Figure 1 This is a schematic diagram of a marine dual gas turbine power branch transmission mechanism according to the present invention; Figure 2 Transmission route diagram for parallel operation of dual gas turbines with single output; Figure 3 A transmission route diagram for the input-output operation of the post-gas turbine; Figure 4 For the dual-output operation transmission route diagram of the post-gas turbine input; Figure 5 This is a transmission route diagram for parallel input and single output operation of the gas turbine and the transverse gear end.

[0013] The diagram shows: 1. First synchronous automatic clutch; 2. Front pinion; 3. Front large gear; 4. First intermediate pinion; 5. Second synchronous automatic clutch; 6. Rear large gear; 7. Rear pinion; 8. Second intermediate pinion; 9. Output gear; 10. Transverse gear; 11. Friction clutch; 21. First shaft; 22. Second shaft; 23. Third shaft; 24. Fourth shaft; 25. Fifth shaft; 26. Sixth shaft; 27. Seventh shaft; 28. Eighth shaft. The dashed lines in each diagram represent the interaction between output gear 9 and the first intermediate pinion 4 and the second intermediate pinion 8, but not the interaction with the fifth shaft 25. Detailed Implementation

[0014] The embodiments of the technical solution of the present invention will now be described in detail with reference to the accompanying drawings. Unless otherwise stated, the technical or scientific terms used in this application should have the ordinary meaning understood by those skilled in the art.

[0015] The following is combined Figure 1 This embodiment of a marine dual gas turbine power branch transmission mechanism includes a shaft assembly, a front gear assembly, a middle gear assembly, and a rear gear assembly. The axis assembly includes a first axis 21, a second axis 22, a third axis 23, a fourth axis 24, a fifth axis 25, a sixth axis 26, a seventh axis 27, and an eighth axis 28; The front gear assembly includes a front pinion 2, a transverse gear 10, and two front large gears 3; a front large gear 3 is installed on the fifth shaft 25 and the seventh shaft 27 respectively; the front pinion 2 installed on the first shaft 21 meshes with the two front large gears 3 respectively; the front large gear 3 installed on the seventh shaft 27 meshes with the transverse gear 10 installed on the eighth shaft 28; the eighth shaft 28 is connected to the end of the transverse gear through a friction clutch 11. The input end of the gas turbine is connected to the first shaft 21 via the first synchronous automatic clutch 1; The intermediate gear assembly includes two first small gears 4 and two second small gears 8, and the rear gear assembly includes a rear small gear 7 and two rear large gears 6. A first small gear 4 is mounted on the fifth shaft 25 and the seventh shaft 27 respectively; a second small gear 8 and a rear large gear 6 are mounted on the fourth shaft 24; a second small gear 8 and a rear large gear 6 are mounted on the sixth shaft 26; and the rear small gear 7 mounted on the second shaft 22 meshes with the two rear large gears 6 respectively. The input end of the gas turbine is connected to the second shaft 22 via the second synchronous automatic clutch 5; An output gear 9 is mounted on the third shaft 23 at the load output end. The output gear 9 meshes with two first pinion gears 4 and two second pinion gears 8 respectively.

[0016] The input of the transverse gear end is arranged coaxially with the eighth shaft 28. The transverse gear end is connected to the eighth shaft 28 through a friction clutch 1 to realize the ability to transmit power from the transmission mechanism of the present invention to the other side of the ship or the power of the other side of the ship to the transmission mechanism of the present invention.

[0017] The design incorporates a three-layer gear assembly, with each assembly featuring multiple gear drives. The overall structure is compact, enhancing the power transmission capacity of the power branch transmission mechanism. This design solves the problems of excessively large and heavy gearboxes, which in turn lead to larger and heavier ships and lower speeds.

[0018] Specifically, the front pinion 2 and the rear pinion 7 have the same gear parameters.

[0019] Specifically, the gear parameters of the front large gear 3 and the rear large gear 6 are the same.

[0020] Specifically, the gear parameters of the first pinion 4 and the second pinion 8 are the same.

[0021] Specifically, the transmission mechanism includes four operating modes: dual gas turbine parallel operation single output mode, single gas turbine input single output mode, single gas turbine input dual output mode, and single gas turbine and transverse gear parallel operation single output mode.

[0022] The above operating modes are explained in detail below: The above operating modes have the following effects / functions: during the mode switching process, while ensuring that the ship speed remains constant, the switching control strategy of the ship's dual gas turbine power branch transmission mechanism can ensure that the total power generated by multiple main engines remains constant, and then switch between multiple operating modes by engaging and disengaging different clutches.

[0023] The term "main unit" here can be understood as follows: Two gas turbines operating in parallel to drive a load have one main unit combination (two main units in front and rear); One gas turbine with a single input and single output has two main unit combination combinations (front main unit or rear main unit); One gas turbine with dual input and dual output has two main unit combination combinations (front main unit input or rear main unit input); One gas turbine with a transverse gear end operating in parallel with a single input and single output has two main unit combination combinations (front main unit input + transverse gear, rear main unit input + transverse gear). The following section introduces the method for switching the operating mode of the power branch transmission of a marine dual gas turbine, based on the power branch transmission mechanism of a marine dual gas turbine. The switching control strategy described below is the switching control between different operating modes.

[0024] Type 1 switching strategy: Control method for switching between dual gas turbine parallel operation with single output and subsequent gas turbine input with single output mode. The dual gas turbine parallel operation with single output mode is: The front gas turbine and the rear gas turbine operate at a speed of R and a power of P, respectively. The first synchronous automatic clutch 1 and the second synchronous automatic clutch 2 are both engaged, and the friction clutch 11 is disengaged. The power of the front gas turbine is transmitted and output sequentially through the first synchronous automatic clutch 1, the front pinion (2), the two front large gears 3, the two first intermediate pinions 4, the two second intermediate pinions 8, and the output gear 9. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6, the two second medium and small gears 8, and the output gear 9; The post-gas turbine input-single-output mode is: The afterburning gas turbine operates at a speed of R and a power output of 2P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6, the two second medium and small gears 8, and the output gear 9; The control strategy for switching from dual gas turbine parallel operation with single output to a single output after gas turbine input is as follows: Friction clutch 11 is not working. First, the power of the front gas turbine is reduced from P to 0, while the power of the rear gas turbine is increased from P to 2P. The total power is kept at 2P. The first synchronous automatic clutch 1 and the second synchronous automatic clutch 5 are kept engaged. Then, the speed of the front gas turbine is reduced from R to 0 to ensure that the first synchronous automatic clutch 1 is disengaged. The second synchronous automatic clutch 5 is kept engaged, thus completing the switching from dual gas turbine parallel operation with single output to the rear gas turbine input with single output. The control strategy for switching from single-output input of the after-gas turbine to parallel operation of dual gas turbines with single output is as follows: Friction clutch 11 is not working. First, the speed of the front gas turbine is increased from 0 to R to ensure that the first synchronous automatic clutch 1 is engaged. Then, the power of the front gas turbine is increased from 0 to P, while the power of the rear gas turbine is reduced from 2P to P, keeping the total power at 2P. After completion, the gas turbine input single output is switched to the working state of dual gas turbine parallel single output.

[0025] The second switching strategy: a control method for switching between dual gas turbine parallel operation with single output and subsequent dual gas turbine input / output modes. The dual gas turbine parallel operation with single output mode is: The front gas turbine and the rear gas turbine operate at a speed of R and a power of P, respectively. The first synchronous automatic clutch 1 and the second synchronous automatic clutch 5 are both engaged, and the friction clutch 11 is disengaged. The power from the gas turbine is transmitted and output sequentially through the first synchronous automatic clutch 1, the front pinion 2, the two front large gears 3, the two first intermediate pinions 4, the two second intermediate pinions 8, and the output gear 9. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6, the two second medium and small gears 8, and the output gear 9; The post-gas turbine input-output dual-output mode is: The afterburning gas turbine operates at a speed of R and a power output of 2P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6, the two second medium and small gears 8, and the output gear 9; The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6 and the two second medium and small gears 8, the output gear 9, the first medium and small gear 4, the front large gear 3, the transverse gear 10 and the friction clutch 11. The control strategy for switching from dual gas turbine parallel operation with single output to dual gas turbine input and dual output is as follows: First, engage the friction clutch 11, then reduce the power P of the front gas turbine to 0, while simultaneously increasing the power of the rear gas turbine from P to 2P, maintaining a total power of 2P. Then, reduce the speed of the front gas turbine from R to 0 to ensure that the first synchronous automatic clutch 1 disengages, completing the switching from dual gas turbine parallel operation with single output to the rear gas turbine input with dual output. The control strategy for switching from dual-output gas turbine input to dual-gas turbine parallel operation with single output is as follows: First, increase the speed of the front gas turbine from 0 to R to ensure that the first synchronous automatic clutch 1 is engaged. Then, increase the power of the front gas turbine from 0 to P, while simultaneously reducing the power of the rear gas turbine from 2P to P, keeping the total power at 2P. Then, disengage the friction clutch 11. After completion, the gas turbine input dual output switches to the working state of dual gas turbine parallel operation single output.

[0026] The third switching strategy: a control method that switches between parallel operation of two gas turbines with single output and parallel operation of the rear gas turbine and the transverse gear end with single output. The dual gas turbine parallel operation with single output mode is: The front gas turbine and the rear gas turbine operate at a speed of R and a power of P, respectively. The first synchronous automatic clutch 1 and the second synchronous automatic clutch 5 are both engaged, and the friction clutch 11 is disengaged. The power from the gas turbine is transmitted and output sequentially through the first synchronous automatic clutch 1, the front pinion 2, the two front large gears 3, the two first intermediate pinions 4, the two second intermediate pinions 8, and the output gear 9. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6, the two second medium and small gears 8, and the output gear 9; The parallel input single output mode of the after-gas turbine and the transverse gear end is: The gas turbine operates at a speed of R and a power output of P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6, the two second medium and small gears 8, and the output gear 9; The transverse gear end moves with a power of P. The power at the transverse gear end is transmitted and output sequentially through the friction clutch 11, the transverse gear 10, the front large gear 3, the first small gear 4, and the output gear 9. The control strategy for switching from parallel operation of two gas turbines with single output to parallel operation of gas turbines and parallel input of the transverse gear end with single output is as follows: First, engage the friction clutch 11, then reduce the power of the front gas turbine from P to 0, while simultaneously increasing the power of the transverse gear end from 0 to P, maintaining a total power of 2P. Then, reduce the speed of the front gas turbine from R to 0, ensuring that the first synchronous automatic clutch 1 disengages, thus completing the switch from parallel operation of gas turbines with single output to parallel operation of the rear gas turbine and transverse gear end with single input. The control strategy for switching the parallel input single output of the rear gas turbine and the transverse gear end to the parallel input single output of the dual gas turbines is as follows: First, increase the speed of the front gas turbine from 0 to R to ensure that the first synchronous automatic clutch 1 is engaged. Then, increase the power of the front gas turbine from 0 to P, while reducing the power of the transverse gear end from P to 0, keeping the total power at 2P. Then, disengage the friction clutch 11. After completion, the parallel input single output of the gas turbine and the transverse gear end is switched to the working state of the dual gas turbines operating in parallel with a single output.

[0027] The fourth switching strategy: The control method for switching between single-output and dual-output inputs of the after-gas turbine is as follows: The post-gas turbine input-single-output mode is: The afterburning gas turbine operates at a speed of R and a power output of 2P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6, the two second medium and small gears 8, and the output gear 9; The post-gas turbine input-output dual-output mode is: The afterburning gas turbine operates at a speed of R and a power output of 2P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6, the two second medium and small gears 8, and the output gear 9; The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6 and the two second medium and small gears 8, the output gear 9, the first medium and small gear 4, the front large gear 3, the transverse gear 10 and the friction clutch 11. The control strategy for switching from a single-output input to a dual-output input of the after-gas turbine is as follows: engage the friction clutch 11 to complete the switching; The control strategy for switching from dual-output to single-output gas turbine input is to disengage the friction clutch 11 to complete the switching.

[0028] The fifth switching strategy: The control method for switching between the input single-output of the after-gas turbine and the parallel input single-output of the after-gas turbine and the transverse gear end is as follows: The post-gas turbine input-single-output mode is: The afterburning gas turbine operates at a speed of R and a power output of 2P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6, the two second medium and small gears 8, and the output gear 9; The parallel input single output mode of the after-gas turbine and the transverse gear end is: The gas turbine operates at a speed of R and a power output of P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch 5, the rear pinion 7, the two rear large gears 6, the two second medium and small gears 8, and the output gear 9; The transverse gear end moves with a power of P. The power at the transverse gear end is transmitted and output sequentially through the friction clutch 11, the transverse gear 10, the front large gear 3, the first small gear 4, and the output gear 9. The control strategy for switching the gas turbine input single output to the parallel input single output of the gas turbine and the transverse gear end is as follows: first, engage the friction clutch 11, then increase the power of the transverse gear end from 0 to P, while simultaneously reducing the power of the gas turbine from 2P to P, keeping the total power at 2P. After completion, the gas turbine input single output is switched to the working state of parallel input single output of the gas turbine and the transverse gear end. The control strategy for switching the parallel input single output of the gas turbine and the transverse gear end to the input single output of the gas turbine is as follows: first, reduce the power of the transverse gear end from P to 0, and at the same time increase the power of the gas turbine from P to 2P. Then, disengage the friction clutch 11. After completion, the parallel input single output of the gas turbine and the transverse gear end is switched to the working state of the input single output of the gas turbine.

[0029] Based on the above operating modes and switching strategies, the following 10 specific implementation methods are provided; For ease of understanding, the names of the various parts are simplified in the text as follows in the embodiments: The first synchronous automatic clutch 1 is simplified to TB1; The second synchronous automatic clutch 2 is simplified to TB2; Friction clutch 11 is simplified to MC.

[0030] The load output terminal is the propeller output terminal.

[0031] Front-side gas turbine is also known as front-side gas turbine; The rear gas turbine is also known as the rear side gas turbine.

[0032] In the following embodiments, mode switching can be performed under various main engine speeds / powers, and the control strategy remains the same. This example uses a specific main engine speed and power level to illustrate the switching control strategy. The following embodiments use a main engine speed R defined as 1500 r / min and a main engine power P defined as 800 kW. In the table below, "engaged" indicates the clutch is engaged, and " / " indicates the clutch is disengaged. In each embodiment below, the total power of the ship remains unchanged before and after switching between the two operating modes to achieve stable ship speed.

[0033] Example 1: Control strategy for switching from dual-gas turbine parallel operation with single output to rear-side gas turbine input with single output: When both main units are driving a single output, the main unit speed is 1500 r / min. The power transfer path at this time is as follows: Figure 2 As shown, clutches TB1 and TB2 are engaged at this time, and each main unit outputs 800kW. When it is necessary to switch to rear-side gas turbine drive single output (such as...) Figure 3 As shown in Table 1, first reduce the power of the front gas turbine to 0, while simultaneously increasing the power of the rear gas turbine to 1600kW (keeping the total power at 1600kW). Then, reduce the speed of the front gas turbine, thus disengaging clutch TB1 and achieving a single-input, single-output operating mode for the rear gas turbine. The switching process is shown in Table 1.

[0034] Table 1. Strategy for switching from dual gas turbine parallel operation to single gas turbine input / output. Example 2: Control strategy for switching from single-output input to dual-gas turbine parallel single-output operation mode. When the rear-side gas turbine operates with a single input / output configuration, the main engine speed is 1500 r / min. At this time, the power transmission path is as follows: Figure 3 As shown, clutch TB2 is engaged at this time, and the main engine outputs 1600kW. When switching to dual-gas turbine parallel operation with single output (as shown in Figure 2), first increase the speed of the front gas turbine to the clutch engagement speed, then clutch TB1 engages, and then increase the power of the front gas turbine to 800kW, while simultaneously reducing the power of the rear gas turbine to 800kW (maintaining a total power of 1600kW), thereby achieving the dual-gas turbine parallel operation with single output mode. See Table 2 for the switching instructions.

[0035] Table 2. Strategy for Switching from Rear Side Gas Turbine Input Single Output to Dual Gas Turbine Parallel Operation Single Output Example 3: Control strategy for switching from dual-gas turbine parallel operation with single output to dual-output operation mode with afterburner input. When the two gas turbines are running in parallel with a single output, the main engine speed is 1500 r / min. The power transmission path at this time is as follows: Figure 2 As shown, clutches TB1 and TB2 are engaged at this time, and each main unit outputs 800kW. When switching to dual output from the rear gas turbine input (e.g.) Figure 4 As shown in Table 3, first engage the friction clutch MC at the transverse gearbox end, then reduce the power of the front gas turbine to 0, while simultaneously increasing the power of the rear gas turbine to 1600kW (maintaining a total power of 1600kW). Then reduce the speed of the front gas turbine to disengage it, thereby achieving the dual-output operation mode of the rear gas turbine input. The switching process is shown in Table 3.

[0036] Table 3. Strategy for switching from single-output to dual-output operation of dual-gas turbines in parallel operation to rear-side gas turbine input. Example 4: Control strategy for switching from dual-output input to dual-output parallel operation mode of the rear gas turbine When the rear-side gas turbine operates with both input and output, the main engine speed is 1500 r / min. At this time, the power transmission path is as follows: Figure 4 As shown, clutches TB2 and MC are engaged at this time, and the main engine outputs 1600kW. When switching to dual-gas turbine parallel operation with single output (as shown in Figure 2), first increase the speed of the front gas turbine to the clutch engagement speed, clutch TB1 engages, then increase the power of the front gas turbine to 800kW, while simultaneously reducing the power of the rear gas turbine to 800kW (maintaining a total power of 1600kW), and then disengage the friction clutch MC, thereby achieving the dual-gas turbine parallel operation with single output mode. See Table 4 for the switching instructions.

[0037] Table 4. Strategy for switching from dual-output input to dual-output parallel operation of the rear gas turbine. Example 5: Control strategy for switching from dual-gas turbine parallel operation with single output to a single-output operation mode with input from the rear gas turbine and the transverse gear end. When the two gas turbines are running in parallel with a single output, the main engine speed is 1500 r / min. The power transmission path at this time is as follows: Figure 2 As shown, clutches TB1 and TB2 are engaged at this time, and each main unit outputs 800kW. When switching to a rear-side gas turbine and a single-output input via the transverse gear end (…), Figure 5 As shown in Table 5, first increase the speed of the transverse gear end to the engagement speed, then engage the friction clutch MC at the transverse gear end (assuming the engagement speed of the transverse gear end is 1000 r / min). Then, reduce the power of the front gas turbine to 0 and simultaneously increase the power of the transverse gear end to 800 kW (maintaining a total power of 1600 kW). After that, reduce the speed of the front gas turbine to disengage it, thereby realizing the single-output input operation mode of the transverse gear end of the rear gas turbine. The switching process is shown in Table 5.

[0038] Table 5. Strategy for switching from dual-gas turbine parallel operation with single output to rear-side gas turbine and transverse gear end input with single output. Example 6: Control Strategy for Switching from Single-Output Input to Dual-Gas-Turbine Parallel Operation with Single-Output at the Rear Gas Turbine and Transverse Gear End. When the rear gas turbine operates in single-output mode at the transverse gear end, the gas turbine speed is 1500 r / min, and the transverse gear end speed is 1000 r / min. The power transmission path at this time is as follows: Figure 5 As shown, at this time, clutches TB2 and MC are engaged, and the main engine outputs 800kW each. When it is necessary to switch to dual-gas turbine parallel operation with single output ( Figure 2 As shown in Table 6, first, increase the speed of the front gas turbine to the clutch engagement speed, engage clutch TB1, then increase the power of the front gas turbine to 800kW, while simultaneously reducing the power at the transverse connection end to 0kW (maintaining a total power of 1600kW), and then disengage the friction clutch, thereby achieving the dual gas turbine parallel operation mode with single output. The switching process is shown in Table 6.

[0039] Table 6. Strategy for switching from single-output input to dual-gas turbine parallel operation at the rear side gas turbine and transverse gear end. Example 7: Control strategy for switching from single-output input to dual-output operation mode of the rear-side combustion engine. When the rear-side gas turbine operates with a single input / output configuration, the main engine speed is 1500 r / min. At this time, the power transmission path is as follows: Figure 3 As shown, clutch TB2 is engaged at this time, and the main engine outputs 1600kW. When it is necessary to switch to dual output from the rear gas turbine ( Figure 4 As shown in Table 7, first engage the friction clutch MC to achieve the dual-output operation mode of the rear gas turbine. Switching is shown in Table 7.

[0040] Table 7. Strategy for Switching Afterburner Input to Dual Afterburner Output Example 8: Control strategy for switching from dual-output rear-side gas turbine input to single-output rear-side gas turbine input operating mode When the rear gas turbine operates with both input and output, the turbine speed is 1500 r / min, and the horizontal connection speed is 1000 r / min. The power transmission path at this time is as follows: Figure 4 As shown, clutches TB2 and MC are engaged at this time, and the main engine outputs 1600kW. When switching to rear-side gas turbine input single output (… Figure 3 As shown in Table 8, disengage the friction clutch MC to achieve the single-output operation mode of the rear gas turbine input. Switching is shown in Table 8.

[0041] Table 8. Strategy for Switching from Dual-Output Rear-Side Gas Turbine Input to Single-Output Rear-Side Gas Turbine Input Example 9: Control strategy for switching from rear-side combustion engine input single output to rear-side combustion engine + transverse input single output operating mode When the rear-side gas turbine operates with a single input / output configuration, the main engine speed is 1500 r / min. At this time, the power transmission path is as follows: Figure 3 As shown, clutch TB2 is engaged at this time, and the main engine outputs 1600kW. When switching to parallel input / single output at the rear gas turbine transverse gear end (…), Figure 5As shown in Table 9, first increase the speed of the transverse gear end to the engagement speed (e.g., 1000 r / min), then engage the friction clutch MC. Next, increase the input power of the transverse end to 800 kW, while simultaneously reducing the power of the rear gas turbine to 800 kW, thereby achieving a single-output operation mode for both the rear gas turbine and the transverse gear end. The switching process is shown in Table 9.

[0042] Table 9. Strategy for Switching Afterburner Input to Afterburner Transverse Gear End Input Single Output Example 10: Control strategy for switching from single-output input to single-output input mode of the rear-side combustion engine and the transverse gear end to the rear-side combustion engine single-output operating mode. When the rear gas turbine and the transverse gear end are operating with a single input / output configuration, the gas turbine speed is 1500 r / min, and the transverse gear end speed is 1000 r / min. The power transmission path at this time is as follows: Figure 5 As shown, clutches TB2 and MC are engaged at this time, and each input terminal outputs 800kW of power. When it is necessary to switch to single output from the rear gas turbine input ( Figure 3 As shown in Table 10, the power at the transverse gear end is first reduced to 0kW, while the power at the rear gas turbine end is increased to 1600kW. Then, the friction clutch MC is disengaged, thereby realizing the single-output operation mode of the rear gas turbine input.

[0043] Table 10. Strategy for Switching from Rear-side Gas Turbine and Transverse Gear Input Single Output to Rear-side Gas Turbine Input Single Output The present invention has been disclosed above with reference to preferred embodiments, but it is not intended to limit the present invention. Any person skilled in the art can make some modifications or alterations to the above-disclosed structure and technical content to create equivalent embodiments without departing from the scope of the present invention, and all such modifications or alterations shall still fall within the scope of the present invention.

Claims

1. A marine dual gas turbine power branch transmission mechanism, characterized in that: It includes a shaft assembly, a front gear assembly, a middle gear assembly, and a rear gear assembly; The axis assembly includes a first axis (21), a second axis (22), a third axis (23), a fourth axis (24), a fifth axis (25), a sixth axis (26), a seventh axis (27), and an eighth axis (28); The front gear assembly includes a front pinion (2), a transverse gear (10), and two front large gears (3); a front large gear (3) is mounted on the fifth shaft (25) and the seventh shaft (27), the front pinion (2) mounted on the first shaft (21) meshes with the two front large gears (3), the front large gear (3) mounted on the seventh shaft (27) meshes with the transverse gear (10) mounted on the eighth shaft (28), and the eighth shaft (28) is connected to the end of the transverse gear through a friction clutch (11). The input end of the gas turbine is connected to the first shaft (21) via the first synchronous automatic clutch (1); The intermediate gear assembly includes two first small gears (4) and two second small gears (8), and the rear gear assembly includes a rear small gear (7) and two rear large gears (6); a first small gear (4) is installed on the fifth shaft (25) and the seventh shaft (27), a second small gear (8) and a rear large gear (6) are installed on the fourth shaft (24), and a second small gear (8) and a rear large gear (6) are installed on the sixth shaft (26). The rear small gear (7) installed on the second shaft (22) meshes with the two rear large gears (6). The input end of the gas turbine is connected to the second shaft (22) via the second synchronous automatic clutch (5); An output gear (9) is installed on the third shaft (23) at the load output end. The output gear (9) meshes with two first small gears (4) and two second small gears (8) respectively.

2. The marine dual gas turbine power branch transmission mechanism according to claim 1, characterized in that: The front pinion (2) and the rear pinion (7) have the same gear parameters.

3. The marine dual gas turbine power branch transmission mechanism according to claim 1, characterized in that: The front gear (3) and the rear gear (6) have the same gear parameters.

4. The marine dual gas turbine power branch transmission mechanism according to claim 1, characterized in that: The gear parameters of the first pinion (4) and the second pinion (8) are the same.

5. The marine dual gas turbine power branch transmission mechanism according to claim 1, characterized in that: The transmission mechanism includes four operating modes: dual gas turbine parallel operation single output mode, single gas turbine input single output mode, single gas turbine input dual output mode, and single gas turbine and transverse gear parallel operation single output mode.

6. A method for switching operating modes of a marine dual gas turbine power branch drive, characterized in that: The method is based on the marine dual gas turbine power branch transmission mechanism according to any one of claims 1 to 4, and the method for switching between the dual gas turbine parallel operation single output and the rear gas turbine input single output modes is as follows: The dual gas turbine parallel operation with single output mode is: The front gas turbine and the rear gas turbine operate at a speed of R and a power of P, respectively. The first synchronous automatic clutch (1) and the second synchronous automatic clutch (5) are both engaged, and the friction clutch (11) is disengaged. The power of the gas turbine is transmitted and output sequentially through the first synchronous automatic clutch (1), the front pinion (2), the two front large gears (3), the two first intermediate pinions (4), the two second intermediate pinions (8), and the output gear (9). The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6), the two second medium and small gears (8), and the output gear (9); The post-gas turbine input-single-output mode is: The afterburning gas turbine operates at a speed of R and a power output of 2P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6), the two second medium and small gears (8), and the output gear (9); The control strategy for switching from dual gas turbine parallel operation with single output to a single output after gas turbine input is as follows: The friction clutch (11) is not working. First, the power of the front gas turbine is reduced from P to 0, and at the same time, the power of the rear gas turbine is increased from P to 2P. The total power is kept at 2P. The first synchronous automatic clutch (1) and the second synchronous automatic clutch (5) are engaged. Then, the speed of the front gas turbine is reduced from R to 0 to ensure that the first synchronous automatic clutch (1) is disengaged and the second synchronous automatic clutch (5) is engaged. The dual gas turbine parallel operation with single output is switched to the rear gas turbine input with single output. The control strategy for switching from single-output input of the after-gas turbine to parallel operation of dual gas turbines with single output is as follows: The friction clutch (11) is not working. First, the speed of the front gas turbine is increased from 0 to R to ensure that the first synchronous automatic clutch (1) is engaged. Then, the power of the front gas turbine is increased from 0 to P, while the power of the rear gas turbine is reduced from 2P to P, keeping the total power at 2P. After completion, the gas turbine input single output is switched to the working state of dual gas turbine parallel single output.

7. A method for switching operating modes of a marine dual gas turbine power branch drive, characterized in that: The method is based on the marine dual gas turbine power branch transmission mechanism according to any one of claims 1 to 4, and the method for switching between the dual gas turbine parallel single output and the rear gas turbine input dual output modes is as follows: The dual gas turbine parallel operation with single output mode is: The front gas turbine and the rear gas turbine operate at a speed of R and a power of P, respectively. The first synchronous automatic clutch (1) and the second synchronous automatic clutch (5) are both engaged, and the friction clutch (11) is disengaged. The power of the gas turbine is transmitted and output sequentially through the first synchronous automatic clutch (1), the front pinion (2), the two front large gears (3), the two first intermediate pinions (4), the two second intermediate pinions (8), and the output gear (9). The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6), the two second medium and small gears (8), and the output gear (9); The post-gas turbine input-output dual-output mode is: The afterburning gas turbine operates at a speed of R and a power output of 2P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6), the two second medium and small gears (8), and the output gear (9); The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6) and the two second medium and small gears (8), the output gear (9), the first medium and small gear (4), the front large gear (3), the transverse gear (10) and the friction clutch (11); The control strategy for switching from dual gas turbine parallel operation with single output to dual gas turbine input and dual output is as follows: First, engage the friction clutch (11), then reduce the power P of the front gas turbine to 0, and at the same time increase the power of the rear gas turbine from P to 2P, keeping the total power at 2P. Then, reduce the speed of the front gas turbine from R to 0, so as to ensure that the first synchronous automatic clutch (1) disengages, and complete the working state of switching the dual gas turbine parallel operation with single output to the rear gas turbine input with dual output. The control strategy for switching from dual-output gas turbine input to dual-gas turbine parallel operation with single output is as follows: First, increase the speed of the front gas turbine from 0 to R to ensure that the first synchronous automatic clutch (1) is engaged. Then, increase the power of the front gas turbine from 0 to P, and at the same time, reduce the power of the rear gas turbine from 2P to P, keeping the total power at 2P. Then, disengage the friction clutch (11). After completion, the gas turbine input dual output is switched to the working state of dual gas turbine parallel operation single output.

8. A method for switching operating modes of a marine dual gas turbine power branch drive, characterized in that: The method is based on the marine dual gas turbine power branch transmission mechanism according to any one of claims 1 to 4, and the method for switching between parallel operation of dual gas turbines with single output and parallel operation of the rear gas turbine and the transverse gear end with single output is as follows: The dual gas turbine parallel operation with single output mode is: The front gas turbine and the rear gas turbine operate at a speed of R and a power of P, respectively. The first synchronous automatic clutch (1) and the second synchronous automatic clutch (5) are both engaged, and the friction clutch (11) is disengaged. The power of the gas turbine is transmitted and output sequentially through the first synchronous automatic clutch (1), the front pinion (2), the two front large gears (3), the two first intermediate pinions (4), the two second intermediate pinions (8), and the output gear (9). The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6), the two second medium and small gears (8), and the output gear (9); The parallel input single output mode of the after-gas turbine and the transverse gear end is: The gas turbine operates at a speed of R and a power output of P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6), the two second medium and small gears (8), and the output gear (9); The transverse gear end moves with a power of P. The power at the transverse gear end is transmitted and output sequentially through the friction clutch (11), transverse gear (10), front large gear (3), first small gear (4) and output gear (9); The control strategy for switching the dual gas turbine parallel operation single output to the gas turbine and the transverse gear end parallel operation input single output is as follows: first, engage the friction clutch (11), then reduce the power of the front gas turbine from P to 0, and at the same time increase the power of the transverse gear end from 0 to P, keeping the total power at 2P. Then, reduce the speed of the front gas turbine from R to 0, ensuring that the first synchronous automatic clutch (1) disengages, and complete the working state of switching the gas turbine parallel operation single output to the rear gas turbine and the transverse gear end parallel operation input single output. The control strategy for switching the parallel input and single output of the rear gas turbine and the transverse gear end to the parallel input and single output of the dual gas turbines is as follows: First, increase the speed of the front gas turbine from 0 to R to ensure that the first synchronous automatic clutch (1) is engaged. Then, increase the power of the front gas turbine from 0 to P, and at the same time, reduce the power of the transverse gear end from P to 0, keeping the total power at 2P. Then, disengage the friction clutch (11). After completion, the parallel input and single output of the gas turbine and the transverse gear end is switched to the working state of the parallel input and single output of the dual gas turbines.

9. A method for switching operating modes of a marine dual gas turbine power branch transmission mechanism, characterized in that: The method is based on the marine dual gas turbine power branch transmission mechanism according to any one of claims 1 to 4, and the method for switching between single-output and dual-output inputs of the rear gas turbine is as follows: The post-gas turbine input-single-output mode is: The afterburning gas turbine operates at a speed of R and a power output of 2P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6), the two second medium and small gears (8), and the output gear (9); The post-gas turbine input-output dual-output mode is: The afterburning gas turbine operates at a speed of R and a power output of 2P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6), the two second medium and small gears (8), and the output gear (9); The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6) and the two second medium and small gears (8), the output gear (9), the first medium and small gear (4), the front large gear (3), the transverse gear (10) and the friction clutch (11); The control strategy for switching from single-output input to dual-output input of the gas turbine is as follows: engage the friction clutch (11) to complete the switching; The control strategy for switching the gas turbine input dual output to the gas turbine input single output is to disengage the friction clutch (11) to complete the switching.

10. A method for switching operating modes of a marine dual gas turbine power branch transmission mechanism, characterized in that: The method is based on the marine dual gas turbine power branch transmission mechanism according to any one of claims 1 to 4, and the method for switching between single-output input from the rear gas turbine and parallel input from the rear gas turbine and the transverse gear end is as follows: The post-gas turbine input-single-output mode is: The afterburning gas turbine operates at a speed of R and a power output of 2P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6), the two second medium and small gears (8), and the output gear (9); The parallel input single output mode of the after-gas turbine and the transverse gear end is: The gas turbine operates at a speed of R and a power output of P. The power of the gas turbine is transmitted and output sequentially through the second synchronous automatic clutch (5), the rear pinion (7), the two rear large gears (6), the two second medium and small gears (8), and the output gear (9); The transverse gear end moves with a power of P. The power at the transverse gear end is transmitted and output sequentially through the friction clutch (11), transverse gear (10), front large gear (3), first small gear (4) and output gear (9); The control strategy for switching the gas turbine input single output to the parallel input single output of the gas turbine and the transverse gear end is as follows: first, engage the friction clutch (11), then increase the power of the transverse gear end from 0 to P, and at the same time reduce the power of the gas turbine from 2P to P, keeping the total power at 2P. After completion, the gas turbine input single output is switched to the working state of the parallel input single output of the gas turbine and the transverse gear end. The control strategy for switching the parallel input and single output of the gas turbine and the transverse gear end to the input and single output of the gas turbine is as follows: first, reduce the power of the transverse gear end from P to 0, and at the same time increase the power of the gas turbine from P to 2P. Then, disengage the friction clutch (11). After completion, the parallel input and single output of the gas turbine and the transverse gear end is switched to the working state of the input and single output of the gas turbine.

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