Power transmission system

Abstract

The present application provides a power transmission system, comprising: a turbine engine; a speed reduction mechanism, wherein the turbine engine is drivingly connected to at least part of the speed reduction mechanism, and the speed reduction mechanism is used for driving a first load to move; and a power change-over mechanism, disposed between the speed reduction mechanism and the first load, wherein the power change-over mechanism has a first power connected state in which the first load is connected to the speed reduction mechanism and a first power disconnected state in which the first load is separated from the speed reduction mechanism. By means of the technical solution provided by the present application, the technical problem in the prior art of short service life of power turbines of turbine engines can be solved.

Description

Drivetrain

[0001] This application claims priority to a patent application filed with the State Intellectual Property Office of China on November 30, 2023, with application number 202311635532.8 and application name “Power Transmission System”. Technical Field

[0002] The present application relates to the technical field of power systems for fracturing equipment, and in particular to a power transmission system. Background Art

[0003] Currently, with the development of fracturing equipment technology, fracturing equipment using turbine engines as power sources has emerged in the existing technology. Turbine engines have many advantages over traditional diesel engines, such as high single-unit power density, the ability to use 100% natural gas as fuel to reduce fuel costs, and more environmentally friendly engine emissions. Turbine engines have an idle operating mode. In this idle operating mode, the compressor turbine in the turbine engine rotates while the power turbine has no power output. When the turbine engine is in idle mode, in order to prevent the fracturing pump from being driven by the power turbine when there is no load or a very low load, a brake is installed on the power output shaft of the high-speed planetary reduction gearbox. Once the turbine engine is in idle mode, the brake forces the power turbine speed to zero.

[0004] However, in idle mode, the turbine engine's air compressor, combustion chamber, and compressor turbine are all running, and a large amount of gas is still discharged from the turbine engine's exhaust port. After exiting the combustion chamber, these gases will first pass through the compressor turbine to drive the compressor turbine to rotate and then drive the air compressor to operate. These gases will then pass through the power turbine to be discharged to the exhaust port. During this process, because the power turbine has been forcibly braked by the brake, these gases need to withstand the high temperature and pressure of the gases when they are discharged through the power turbine, which will affect the service life of the power turbine and shorten its service life.

[0005] Summary of the Invention

[0006] The main purpose of the present application is to provide a power transmission system to solve the technical problem of short service life of the power turbine of the turbine engine in the prior art.

[0007] In order to achieve the above objectives, the present application provides a power transmission system, comprising:

[0008] turbine engines;

[0009] a speed reduction mechanism, the turbine engine being drivingly connected to at least a portion of the speed reduction mechanism, the speed reduction mechanism being configured to drive the first load to move;

[0010] The power conversion mechanism is provided between the speed reduction mechanism and the first load, and has a first power connection state for connecting the first load to the speed reduction mechanism and a first power disconnection state for disconnecting the first load from the speed reduction mechanism.

[0011] Furthermore, the power conversion mechanism includes:

[0012] A first clutch, the first clutch is used to disengage or engage with the speed reduction mechanism; or,

[0013] The first clutch and the first brake; when the first clutch is disengaged from the reduction mechanism, the first brake is used to brake the power output part of the power conversion mechanism or the power input part of the first load; when the first clutch is engaged with the reduction mechanism, the first brake releases the brake on the power output part of the power conversion mechanism or the power input part of the first load.

[0014] Furthermore, the speed reduction mechanism includes:

[0015] A first reduction structure and a second load, the turbine engine is drivingly connected to the first reduction structure, the first reduction structure has a first power output end and a second power output end, the first power output end is drivingly connected to the first load, the second power output end is drivingly connected to the second load, and the first reduction structure can be selectively drivingly connected to the first load and / or the second load.

[0016] Furthermore, the second load is a generator or a motor.

[0017] Furthermore, the power transmission system further includes:

[0018] The speed regulating mechanism includes a second reduction gear structure and a speed regulating motor. The second reduction gear structure has a first power input end and a second power input end. The first power input end can be selectively connected to or disconnected from the first power output end. The power output part of the second reduction gear structure is drive-connected to the first load. The second power input end can be selectively connected to or disconnected from the power output part of the speed regulating motor. The second load is used to be selectively connected to the speed regulating motor to power the speed regulating motor.

[0019] Furthermore, the speed regulating mechanism further comprises:

[0020] The switching mechanism is arranged between the second power input end and the speed regulating motor. The switching mechanism has a second power connection state that connects the second power input end to the speed regulating motor and a second power disconnection state that disconnects the second power input end from the speed regulating motor.

[0021] Furthermore, the switching mechanism includes:

[0022] A second clutch, the second clutch is used to disengage or engage with the speed regulating motor;

[0023] The second brake is connected to the second clutch; when the second clutch is disengaged from the speed regulating motor, the second brake is used to brake the second power input end; when the second clutch is engaged with the speed regulating motor, the second brake releases the brake on the second power input end.

[0024] Furthermore, the first deceleration structure includes:

[0025] a first power input shaft, the first power input shaft forming a power input portion of the first reduction gear structure;

[0026] a first planetary gear structure, wherein a power input portion of the first planetary gear structure is connected to a power input shaft;

[0027] a first power output shaft connected to the power output portion of the first planetary gear structure, the first power output shaft forming a first power output end;

[0028] The first parallel gear set is connected to the first power output shaft, and the power output part of the first parallel gear set forms the second power output end.

[0029] Furthermore, the first planetary gear structure includes:

[0030] The first sun gear, the first planetary gear, the first planetary carrier and the first ring gear, the first planetary gear is engaged with the first sun gear, the first planetary gear is installed on the first planetary carrier, the first planetary carrier is fixed, the first planetary gear drives the first ring gear to rotate, and the first ring gear is connected to the first power output shaft.

[0031] Furthermore, the first deceleration structure further includes:

[0032] The starter motor is selectively connected to or disconnected from the first planetary gear, so as to drive the first planetary gear to move or be disconnected from the first planetary gear through the starter motor.

[0033] Furthermore, the first deceleration structure further includes:

[0034] a second parallel gear set, the second parallel gear set being arranged between the starter motor and the first planetary gear, the first power connection portion of the second parallel gear set being connected to the starter motor, and the second power connection portion of the second parallel gear set being connected to the first planetary gear;

[0035] a third clutch disposed between the power input portion of the second parallel gear set and the starter motor;

[0036] Among them, when the speed of the starter motor is greater than the speed of the first power connection part, the third clutch engages to enable the starter motor to drive the first power connection part to rotate; when the speed of the starter motor is less than the speed of the first power connection part, the third clutch disengages to disconnect the starter motor from the first power connection part.

[0037] Furthermore, the second deceleration structure includes:

[0038] a second power input shaft and a third power input shaft, the second power input shaft having a first power input end, and the third power input shaft having a second power input end;

[0039] a second planetary gear structure, the second planetary gear structure comprising a second sun gear, second planetary gears, a second planetary carrier and a second ring gear, the second planetary gear being meshed with the second sun gear, the second planetary gear being mounted on the second planetary carrier, the second planetary carrier and the second sun gear being connected to the second power input shaft, and the second ring gear being connected to the third power input shaft;

[0040] The second power output shaft is connected to the second planetary carrier, and the second power output shaft forms a power output part of the second reduction gear structure.

[0041] Furthermore, the second deceleration structure further includes:

[0042] The transmission gear is connected to the third power input shaft, and the transmission gear is engaged with the second ring gear, so that the third power input shaft is connected to the second ring gear through the transmission gear.

[0043] Further, the first load is a plunger pump;

[0044] Wherein, the plunger pump includes a third parallel gear set and a hydraulic end connected; the power output part of the second reduction structure is connected to the power input part of the third parallel gear set; or,

[0045] The plunger pump includes a third parallel gear set, a third planetary gear structure and a hydraulic end connected in sequence; the speed regulating mechanism is arranged between the third parallel gear set and the third planetary gear structure, and the third parallel gear set is arranged between the first power input end and the first power output end, so that the first power input end is connected to the first power output end through the third parallel gear set; the power output part of the second reduction structure is connected to the power input part of the third planetary gear structure.

[0046] By applying the technical solution of the present application and setting a power conversion mechanism, the first load can have a first power state connected to the reduction mechanism and a first power disconnection state in which the first load is separated from the reduction mechanism, thereby facilitating the connection and disconnection of power, and avoiding the forced braking of the power turbine of the turbine engine in idle mode, which causes the power turbine to be subjected to the high temperature and pressure of the fuel gas, so that the power turbine can rotate naturally under the action of the fuel gas, thereby avoiding the technical problem of shortening the service life of the power turbine due to forced braking of the power turbine. BRIEF DESCRIPTION OF THE DRAWINGS

[0047] The drawings that constitute part of this application are used to provide a further understanding of this application. The illustrative embodiments of this application and their descriptions are used to explain this application and do not constitute an improper limitation on this application. In the drawings:

[0048] FIG1 shows a schematic structural diagram of a power transmission system without a speed regulating mechanism according to an embodiment of the present application;

[0049] FIG2 shows a schematic structural diagram of a power transmission system without a speed regulating mechanism according to another embodiment of the present application;

[0050] FIG3 shows a schematic structural diagram of a power transmission system according to an embodiment of the present application;

[0051] FIG4 shows a schematic structural diagram of a power conversion mechanism provided according to an embodiment of the present application;

[0052] FIG5 shows a schematic structural diagram of a speed reduction mechanism provided according to an embodiment of the present application;

[0053] FIG6 shows a schematic structural diagram of a speed regulating mechanism provided according to an embodiment of the present application;

[0054] FIG7 shows a schematic structural diagram of a plunger pump according to an embodiment of the present application;

[0055] FIG8 shows a schematic structural diagram of a power transmission system according to another embodiment of the present application;

[0056] FIG9 shows a schematic structural diagram of a plunger pump provided according to another embodiment of the present application.

[0057] The above drawings include the following reference numerals: 10, turbine engine; 11, compressor; 12, combustion chamber; 13, compressor turbine; 14, power turbine; 20, speed reduction mechanism; 21, first speed reduction structure; 211, first power input shaft; 212, first planetary gear structure; 2121, first sun gear; 2122, first planetary gear; 2123, first planetary carrier; 2124, first ring gear; 213, first power output shaft; 214, first parallel gear set; 215, starter motor; 216, second parallel gear set; 217, third clutch; 22, second load; 30, speed regulating mechanism; 31, second speed reduction structure; 311, second power input shaft; 312, third power input shaft; 313, Second planetary gear structure; 3131, second sun gear; 3132, second planetary gear; 3133, second planetary carrier; 3134, second ring gear; 314, second power output shaft; 315, transmission gear; 32, speed regulating motor; 33, switching mechanism; 331, second clutch; 332, second brake; 40, power conversion mechanism; 41, first clutch; 42, first brake; 50, plunger pump; 51, third parallel gear set; 52, third planetary gear structure; 53, hydraulic end. DETAILED DESCRIPTION

[0058] It should be noted that, in the absence of conflict, the embodiments and features of the embodiments in this application can be combined with each other. The present application will be described in detail below with reference to the accompanying drawings and in conjunction with the embodiments.

[0059] As shown in Figures 1 to 9, an embodiment of the present application provides a power transmission system, which includes a turbine engine 10, a reduction gear 20, and a power conversion mechanism 40. The turbine engine 10 is drivingly connected to at least a portion of the reduction gear 20, and the reduction gear 20 is used to drive a first load. The power conversion mechanism 40 is disposed between the reduction gear 20 and the first load, and the power conversion mechanism 40 has a first power connection state in which the first load is connected to the reduction gear 20, and a first power disconnection state in which the first load is disconnected from the reduction gear 20.

[0060] By adopting the power transmission system provided in this embodiment, the power conversion mechanism 40 can enable the first load to have a first power state in which it is connected to the reduction mechanism 20 and a first power disconnection state in which the first load is separated from the reduction mechanism 20, thereby facilitating the connection and disconnection of power and avoiding the forced braking of the power turbine of the turbine engine 10 in the idle mode, which causes the power turbine to be subjected to the high temperature and pressure of the fuel gas, so that the power turbine can rotate naturally under the action of the fuel gas, thereby avoiding the technical problem of shortening the service life of the power turbine due to forced braking of the power turbine.

[0061] Specifically, the power conversion mechanism 40 includes a first clutch 41, which is used to disengage or engage with the reduction mechanism 20. Alternatively, the power conversion mechanism 40 includes the first clutch 41 and a first brake 42. When the first clutch 41 is disengaged from the reduction mechanism 20, the first brake 42 is used to brake the power output of the power conversion mechanism 40 or the power input of the first load. When the first clutch 41 is engaged with the reduction mechanism 20, the first brake 42 releases the brake on the power output of the power conversion mechanism 40 or the power input of the first load. This structural arrangement facilitates effective separation during braking, preventing the turbine engine 10 from continuing to affect its operation while braking. Specifically, when the turbine engine 10 is a dual-shaft turbine engine 10 in idle mode, engaging the clutch and braking simultaneously can effectively reduce the impact of braking on the power turbine, which could affect the turbine's service life, compared to braking alone.

[0062] The power conversion mechanism 40 operates by disengaging or engaging the power transmitted from the power input portion of the power conversion mechanism 40 via the first clutch 41. The first brake 42 brakes the power output portion of the power conversion mechanism 40 when the first clutch 41 is disengaged and releases the brakes when the first clutch 41 is engaged.

[0063] Specifically, the turbine engine 10 in this embodiment includes a compressor 11 , a combustion chamber 12 , a compressor turbine 13 and a power turbine 14 .

[0064] In this embodiment, the reduction mechanism 20 includes a first reduction mechanism 21 and a second load. The turbine engine 10 is driven and connected to the first reduction mechanism 21. The first reduction mechanism 21 has a first power output end and a second power output end. The first power output end is driven and connected to the first load, and the second power output end is driven and connected to the second load. The first reduction mechanism 21 can be selectively driven and connected to the first load and / or the second load. Specifically, the first reduction mechanism 21 can be driven and connected to the first load; or the first reduction mechanism 21 can be driven and connected to the second load; or the first reduction mechanism 21 can be driven and connected to the first load and the second load to drive the first load and the second load to operate. In this way, the operating conditions of the first load and the second load can be flexibly adjusted according to actual operating conditions.

[0065] Specifically, the second load is a generator, a motor, or a starter-generator integrated machine.

[0066] In this embodiment, the power transmission system further includes a speed regulating mechanism 30, which includes a second reduction gear structure 31 and a speed regulating motor 32. The second reduction gear structure 31 has a first power input end and a second power input end. The first power input end can be selectively connected to or disconnected from the first power output end. The power output portion of the second reduction gear structure 31 is drivingly connected to a first load, and the second power input end can be selectively connected to or disconnected from the power output portion of the speed regulating motor 32. The second load 22 is configured to be selectively connected to the speed regulating motor 32 to supply power to the speed regulating motor 32. Using the speed regulating mechanism 30 for speed regulation eliminates the need to restrict the turbine engine 10 to having a speed regulating function. Instead, the turbine engine 10 can be selected based on the required dimensions and weight, thereby increasing the selection range of the turbine engine 10.

[0067] In this embodiment, the power transmission system has three different operating modes, corresponding to pure electric mode, pure engine mode and hybrid mode. For the pure electric mode, the generator is connected to the speed regulating motor 32 to supply power to the speed regulating motor 32, the first power input terminal is disconnected from the first power output terminal, and the second power input terminal is connected to the power output of the speed regulating motor 32. For the pure engine mode, the first power input terminal is connected to the first power output terminal, and the second power input terminal is disconnected from the power output of the speed regulating motor 32. For the hybrid mode, the first power input terminal is connected to the first power output terminal, and the second power input terminal is connected to the power output of the speed regulating motor 32. In this way, it is convenient to select different modes to drive the driven parts according to actual usage requirements.

[0068] Specifically, the turbine engine 10 can be a single-shaft, dual-shaft, or triple-shaft turbine engine 10, and the turbine engine 10 can be a gas turbine engine. The generator can be a common generator or a starter-generator integrated machine.

[0069] In this embodiment, the speed regulating mechanism 30 further includes a switching mechanism 33, which is disposed between the second power input terminal and the speed regulating motor 32. The switching mechanism 33 has a second power connection state in which the second power input terminal is connected to the speed regulating motor 32, and a second power disconnection state in which the second power input terminal is disconnected from the speed regulating motor 32. This structural arrangement facilitates switching the second power input terminal to different states of connection or disconnection with the speed regulating motor 32, thereby facilitating smooth switching and thereby facilitating switching the power transmission system to different operating modes.

[0070] Specifically, the switching mechanism 33 includes a second clutch 331 and a second brake 332. The second clutch 331 is used to disengage or engage with the speed regulating motor 32. The second brake 332 is connected to the second clutch 331. When the second clutch 331 is disengaged from the speed regulating motor 32, the second brake 332 is used to brake the second power input terminal. When the second clutch 331 is engaged with the speed regulating motor 32, the second brake 332 releases the brake on the second power input terminal. This structural arrangement facilitates effective clutching and engaging during braking, avoiding the situation where braking affects the service life of the speed regulating motor 32, thereby improving the service life of the speed regulating motor 32.

[0071] In this embodiment, the first reduction gear structure 21 includes: a first power input shaft 211, a first planetary gear structure 212, a first power output shaft 213, and a first parallel gear set 214. The first power input shaft 211 forms the power input portion of the first reduction gear structure 21, and the power input portion of the first planetary gear structure 212 is connected to the power input shaft; the first power output shaft 213 is connected to the power output portion of the first planetary gear structure 212, and the first power output shaft 213 forms a first power output end; the first parallel gear set 214 is connected to the first power output shaft 213, and the power output portion of the first parallel gear set 214 forms a second power output end. Such a structural arrangement facilitates effective deceleration operation and facilitates the formation of the first power output end and the second power output end, thereby facilitating effective power output switching.

[0072] Specifically, the first planetary gear structure 212 in this embodiment includes a first sun gear 2121, first planetary gears 2122, a first planet carrier 2123, and a first ring gear 2124. The first planetary gears 2122 mesh with the first sun gear 2121. The first planetary gears 2122 are mounted on the first planet carrier 2123, which is fixed. The first planetary gears 2122 drive the first ring gear 2124 to rotate, and the first ring gear 2124 is connected to the first power output shaft 213. This structural arrangement is simple and facilitates stable deceleration operation.

[0073] In this embodiment, the first reduction mechanism 21 further includes a starter motor 215, which can be selectively connected or disconnected with the first planetary gear 2122, so that the starter motor 215 can drive the first planetary gear 2122 to move or disconnect from the first planetary gear 2122. This structural arrangement facilitates providing external starting assistance, facilitates stable starting of the first planetary gear 2122, and facilitates disconnection from the starter motor 215 after the first planetary gear 2122 has stabilized. Specifically, the starter motor 215 can be a turbine engine starter motor.

[0074] Specifically, the first reduction mechanism 21 in this embodiment further includes a second parallel gear set 216 and a third clutch 217. The second parallel gear set 216 is disposed between the starter motor 215 and the first planetary gear 2122. The first power connection portion of the second parallel gear set 216 is connected to the starter motor 215, and the second power connection portion of the second parallel gear set 216 is connected to the first planetary gear 2122. The third clutch 217 is disposed between the power input portion of the second parallel gear set 216 and the starter motor 215. When the speed of the starter motor 215 is greater than the speed of the first power connection portion, the clutch engages to allow the starter motor 215 to drive the first power connection portion to rotate. When the speed of the starter motor 215 is less than the speed of the first power connection portion, the clutch disengages to disconnect the starter motor 215 from the first power connection portion. Such a structural setting can effectively increase the speed of the first planetary gear 2122 when the speed of the first planetary gear 2122 is low; after the speed of the first planetary gear 2122 is successfully started, it is smoothly separated from the starter motor 215, avoiding the influence of the starter motor 215 on the operation of the first planetary gear 2122.

[0075] Specifically, the working principle of the reduction mechanism 20 is as follows: the power from the upstream is input by the first power input shaft 211, driving the first sun gear 2121 to operate, the first sun gear 2121 drives the first planetary gear 2122 to operate, the first planetary carrier 2123 remains fixed, the first planetary gear 2122 drives the first ring gear 2124 to operate, and the first ring gear 2124 drives the first power output shaft 213 to operate to realize the output of the main power. In addition, the first power output shaft 213 also drives the generator or the starter generator through the first parallel gear set 214 to realize the power generation function. The generator mainly supplies power to the motor. There is a clutch between the starter motor 215 and the second parallel gear set 216. Once the output speed of the second parallel gear set 216 exceeds the speed of the starter motor 215, the clutch will automatically disengage.

[0076] In this embodiment, the second reduction gear mechanism 31 includes a second power input shaft 311, a third power input shaft 312, a second planetary gear mechanism 313, and a second power output shaft 314. The second power input shaft 311 has a first power input end, and the third power input shaft 312 has a second power input end. The second planetary gear mechanism 313 includes a second sun gear 3131, second planetary gears 3132, a second planetary carrier 3133, and a second ring gear 3134. The second planetary gears 3132 mesh with the second sun gear 3131. The second planetary gears 3132 are mounted on the second planetary carrier 3133. The second planetary carrier 3133 and the second sun gear 3131 are connected to the second power input shaft 311, and the second ring gear 3134 is connected to the third power input shaft 312. The second power output shaft 314 is connected to the second planetary carrier 3133, forming the power output portion of the second reduction gear mechanism 31. Such a structural arrangement can facilitate the smooth optimization of the layout of the power input and output of the second deceleration structure 31, thereby facilitating the optimization of the deceleration structure and smoothly achieving the deceleration and speed regulation effects.

[0077] Specifically, the second reduction gear mechanism 31 further includes a transmission gear 315, the third power input shaft 312 is connected to the transmission gear 315, and the transmission gear 315 meshes with the second ring gear 3134, so that the third power input shaft 312 is connected to the second ring gear 3134 via the transmission gear 315. Specifically, the transmission gear 315 meshes with the external teeth of the second ring gear 3134, so that the transmission gear 315 can smoothly drive the second ring gear 3134 to move, thereby facilitating smooth speed regulation and effectively achieving a speed regulation effect.

[0078] The operating principle of the speed control mechanism 30 is as follows: power from upstream is input through the second power input shaft 311, which in turn drives the second sun gear 3131 to rotate. The second sun gear 3131 then drives the second planetary gears 3132 to rotate, which in turn rotates the second planetary carrier 3133, which in turn rotates the second power output shaft 314. Furthermore, the speed of the second ring gear 3134 is driven by the speed control motor 32. Based on the equation for a single-row planetary gear: nsun + αnannulus - (1 + α)ncarrier = 0, where nsun is the sun gear speed; nannulus is the ring gear speed; ncarrier is the planetary carrier speed; and α is the ratio of the number of ring gear teeth, zannulus, to the number of sun gear teeth, zsun, i.e., α = zannulus / zsun, with α > 1. Therefore, the speed of the second planetary carrier 3133, ncarrier = (nsun + αnannulus) / (1 + α). Based on the above formula, when the speed-regulating motor 32 is outputting no speed, the second clutch 331 disengages the power input from the speed-regulating motor 32, and the second brake 332 applies the brake to the second ring gear 3134, meaning that the speed of the second ring gear 3134 is zero. At this point, the speed of the second planetary carrier 3133, ncarrier, equals n sun / (1 + α). This means that the output speed of the planetary gearbox is determined solely by the speed ratio α between the second ring gear 3134 and the second sun gear 3131. When the speed-regulating motor 32 is operating, the second clutch 331 engages the power input from the speed-regulating motor 32, and the second brake 332 applies the brake to the second ring gear 3134. This allows the speed-regulating motor 32 to drive the second ring gear 3134 to rotate via the second clutch 331 and the transmission gear 315. At this time, the rotational speed of the second planetary carrier 3133 is ncarrier = (nsun + αnannulus) / (1 + α). When the rotational speed of the second speed-regulating motor 32 is the highest, that is, when the rotational speed of the corresponding second ring gear 3134 is the highest, the rotational speed of the planetary carrier, that is, the output rotational speed of the speed-regulating reduction gearbox, reaches the maximum.

[0079] In this embodiment, the power transmission system further includes a plunger pump 50 , which forms a driven component.

[0080] Specifically, the plunger pump 50 includes a third parallel gear set 51 and a hydraulic end 53 that are connected to each other; the power output portion of the second reduction mechanism 31 is connected to the power input portion of the third parallel gear set 51 .

[0081] Alternatively, the plunger pump 50 includes a third parallel gear set 51, a third planetary gear structure 52, and a hydraulic end 53, which are connected in sequence. The speed regulating mechanism 30 is disposed between the third parallel gear set 51 and the third planetary gear structure 52. The third parallel gear set 51 is disposed between the first power input end and the first power output end, such that the first power input end is connected to the first power output end via the third parallel gear set 51; and the power output portion of the second reduction gear structure 31 is connected to the power input portion of the third planetary gear structure 52.

[0082] Specifically, the plunger pump 50 operates as follows: upstream power is input through the pump's power input port, reduced in speed by the third parallel gear set 51 and the third planetary gear structure 52, and then drives the crankshaft within the pump's power output port, which in turn drives the plunger. Low-pressure suction and high-pressure injection are achieved through the hydraulic end 53.

[0083] As shown in Figures 1 and 2, the power transmission system in this embodiment does not include a speed regulating mechanism 30. The first reduction mechanism 21 can be a high-speed reduction gearbox. A power take-off port is installed on the high-speed reduction gearbox to drive the load, and a clutch is installed on the power transmission system between the power output of the high-speed reduction gearbox and the power input of the fracturing pump. This allows the turbine engine to rotate freely to drive the generator to generate electricity without overspeeding in idle mode, thereby avoiding potential impact on the life of the turbine engine.

[0084] The difference between the power transmission system in Figure 1 and the power transmission system in Figure 2 lies in the different specific arrangements of the power conversion mechanism 40. As shown in Figure 1, the first clutch 41 and the first brake 42 can be combined into one component, and the installation position is between the power output end of the high-speed reduction gearbox and the power input end of the fracturing plunger pump. As shown in Figure 2, the first clutch 41 is arranged between the power output end of the high-speed reduction gearbox and the power input end of the fracturing plunger pump, and the first brake 42 is spaced apart from the first clutch 41, and the first brake 42 is connected to the power input end of the fracturing plunger pump. The main working principle is to disengage or engage the power transmitted from the power input end of the high-speed reduction gearbox through the first clutch 41. The first brake 42 is responsible for braking the power output end when the first clutch 41 is disengaged, and releasing the brake on the power output end when the first clutch 41 is engaged.

[0085] The working principle of a high-speed reduction gearbox is as follows: power from upstream is input through the power input shaft, which drives the sun gear, which in turn drives the planetary gears. The planetary carrier remains fixed, and the planetary gears drive the ring gear, which in turn drives the power output shaft to achieve the main power output. In addition, the power output shaft also drives the generator or starter generator through parallel gears to achieve power generation.

[0086] The main working process of the power transmission system is described as follows:

[0087] Normal Operation Pumping Mode of the Fracturing Plunger Pump: In this normal operation mode, the turbine engine 10's power output is reduced in speed and increased in torque by the high-speed reduction gearbox. This not only drives the second load 22, but also drives the fracturing plunger pump via the drive shaft and first clutch 41. At this time, the first clutch 41 is engaged, and the first brake 42 is not in its braking state.

[0088] Turbine engine idle mode: When the turbine engine is in idle mode, the turbine engine 10 is in idle mode, the second load 22 is in working state, the first clutch 41 is in disengaged state, and the first brake 42 is in braking state.

[0089] Turbine engine shutdown mode: When the turbine engine is in the shutdown mode, the first brake 42 is in a non-braking state, so as to facilitate the operator to perform cranking maintenance on the fracturing plunger pump.

[0090] As shown in Figures 3 to 7, in one embodiment, the power output part of the second reduction gear structure 31 is connected to the power input part of the third parallel gear set 51. It can also be understood that the speed regulating mechanism 30 and the plunger pump 50 are two independent structures, which facilitates the selection of the speed regulating mechanism 30.

[0091] In this embodiment, the corresponding power transmission system operates as follows: the power output of the gas turbine engine 10 is reduced in speed and increased in torque by a high-speed reduction gearbox (corresponding to the reduction mechanism 20), then passes through a power converter and a speed-regulating planetary reduction gearbox (corresponding to the speed-regulating mechanism 30) for further reduction in speed and increased in torque, thereby driving the fracturing plunger pump 50. The operating modes of this power transmission system are specifically categorized as follows:

[0092] 1) Pure Electric Mode—The operating mode of the fracturing pump is purely electric. In this mode, the first clutch 41 of the power converter is disengaged, preventing the gas turbine engine 10's output power from being transmitted to the speed-regulating planetary reduction gearbox and the fracturing plunger pump 50. Simultaneously, the first brake 42 of the power converter brakes the first sun gear 2121 of the speed-regulating planetary reduction gearbox. In this mode, the gas turbine engine 10 can drive the high-speed reduction gearbox. Since the high-speed reduction gearbox is equipped with a generator, this mode also enables power generation. Furthermore, in this mode, the first clutch 41 of the speed-regulating planetary reduction gearbox is engaged, and the second brake 332 releases the second ring gear 3134. The motor drives the second ring gear 3134, which in turn drives the second planetary gears 3132. Power is then output from the second power output shaft 314 through the second planetary carrier 3133, driving the fracturing pump. In this operating mode, flow control of the fracturing pump is achieved through motor speed regulation. The generator installed in the high-speed reduction gearbox can also power the motor installed in the speed-regulating planetary reduction gearbox.

[0093] 2) Pure Engine Mode—The gas turbine engine 10 directly drives the fracturing pump. In this mode, the first clutch 41 of the power converter is engaged, and the first brake 42 is released. The motor on the planetary speed reduction gearbox stops, the second clutch 331 is disengaged, and the second brake 332 applies the brake to the second ring gear 3134. The output power of the gas turbine engine 10 directly drives the fracturing plunger pump 50 through the high-speed reduction gearbox and the planetary speed reduction gearbox.

[0094] 3) Hybrid mode - hybrid mode of turbine direct drive + motor speed regulation. This mode starts the motor speed regulation mode on the basis of the turbine direct drive working mode. Specifically, the first clutch 41 of the power converter is engaged, and the first brake 42 is released. The second clutch 331 on the speed regulating planetary reduction box is engaged, and the second brake 332 releases the brake on the second ring gear 3134. The speed regulating motor 32 is running, thereby driving the second ring gear 3134 to operate. Based on the single-row planetary gear equation of the planetary gearbox, the speed n of the second planet carrier 3133 in this mode is carrier =(n sun +αn annulus ) / (1+α), when the speed of the speed regulating motor 32 is the highest, that is, when the speed of the corresponding second ring gear 3134 is the highest, the speed of the second planetary carrier 3133, that is, the output speed of the speed regulating reduction gearbox reaches the maximum.

[0095] As shown in Figures 8 and 9, in another embodiment, the speed regulating mechanism 30 is disposed between the third parallel gear set 51 and the third planetary gear structure 52. The third parallel gear set 51 is disposed between the first power input end and the first power output end, such that the first power input end is connected to the first power output end via the third parallel gear set 51; and the power output portion of the second reduction gear structure 31 is connected to the power input portion of the third planetary gear structure 52. It can also be understood that the speed regulating mechanism 30 and the plunger pump 50 are integrated into an integral structure, which facilitates integrated installation and operation and simplifies the operator's operation process.

[0096] In this embodiment, the main operating principle is as follows: power from upstream is input through the power input portion of the plunger pump 50. After initial speed reduction by the third parallel gear set 51, the power is transmitted to the third sun gear of the third planetary gear structure 52. After speed reduction and torque increase by the speed-regulating planetary reduction box, the power is output by the third planetary carrier of the third planetary gear structure 52, driving the third sun gear of the third planetary reduction assembly through the third power input shaft 312. The third sun gear drives the third planetary gear. Since the third ring gear of the third planetary gear structure 52 is fixed, the power is output through the third planetary carrier and the third power output shaft, driving the crankshaft of the fracturing plunger pump 50. The second planetary gear structure 313 is integrated between the third parallel gear set 51 and the third planetary gear structure 52 of the fracturing plunger pump 50.

[0097] In summary, the power transmission system operates as follows: the power output of the gas turbine engine 10 is reduced in speed and increased in torque by the high-speed reduction gearbox (reduction mechanism 20), and then driven by the power converter to operate the fracturing plunger pump 50. The reduction gearbox of the fracturing plunger pump 50 specifically includes a third parallel gear set 51, a speed regulating mechanism 30, and a third planetary gear structure 52. Furthermore, the power transmission system has the following operating modes:

[0098] 1) Pure Electric Mode—The operating mode of the fracturing pump is purely electric. In this mode, the first clutch 41 of the power converter is disengaged, preventing the output power of the gas turbine engine 10 from being transmitted to the fracturing plunger pump 50. Simultaneously, the first brake 42 of the power converter brakes the driving gear within the third parallel gear set 51 of the fracturing plunger pump 50, thereby braking the second sun gear 3131 of the speed control mechanism 30. In this mode, the gas turbine engine 10 can drive the high-speed reduction gearbox. Since the high-speed reduction gearbox is equipped with a generator, this mode can also achieve power generation. In this mode, the second clutch 331 on the second planetary gear structure 313 mounted on the fracturing plunger pump 50 engages, and the second brake 332 releases the second ring gear 3134 on the second planetary gear structure 313. The motor drives the second ring gear 3134, which in turn drives the second planetary gear 3132. Since the second sun gear 3131 is braked, power is output from the second power output shaft 314 via the second planetary carrier 3133, thereby driving the third sun gear of the third planetary gear structure 52. The third sun gear drives the third planetary gear, and power then passes through the third planetary carrier and the third power output shaft of the third planetary gear structure 52 to drive the crankshaft of the fracturing pump. In this operating mode, flow regulation of the fracturing pump can be achieved by regulating the speed of the speed-regulating motor 32. The generator mounted on the reduction mechanism 20 can also power the speed-regulating motor 32 mounted on the second reduction mechanism 31.

[0099] 2) Pure engine mode—an operating mode in which the pure turbine engine 10 directly drives the fracturing pump. In this mode, the second clutch 331 of the power converter is engaged, and the second brake 332 is released. The motor on the second reduction gear mechanism 31 stops running, the second clutch 331 is disengaged, and the second brake 332 brakes the second ring gear 3134. The second sun gear 3131 of the second reduction gear mechanism 31 operates normally. The output power of the gas turbine engine 10 is directly input to the power input end of the fracturing plunger pump 50 through the high-speed reduction box and the power converter. In this operating mode, the second ring gear 3134 of the second reduction gear mechanism 31 is in a braking state and has no speed regulation function.

[0100] 3) Hybrid mode - a hybrid mode of turbine direct drive + motor speed regulation. This mode starts the motor speed regulation mode on the basis of the above-mentioned turbine direct drive working mode. Specifically, the first clutch 41 of the power converter is engaged, and the first brake 42 is released. The second clutch 331 on the speed regulating mechanism 30 is engaged, and the second brake 332 releases the brake on the second ring gear 3134. The speed regulating motor 32 runs, thereby driving the ring gear to run. Based on the single-row planetary gear equation of the planetary gearbox, in this mode, the speed of the second planetary carrier 3133 is ncarrier=(nsun+αnannulus) / (1+α). When the speed of the speed regulating motor 32 is the highest, that is, when the speed of the second ring gear 3134 is the highest, the speed of the second planetary carrier 3133, that is, the speed of the second power output shaft 314 of the second reduction gear structure 31 reaches the maximum.

[0101] From the above description, it can be seen that the above embodiments of the present application achieve the following technical effects: expanding the selection range of turbine engines and increasing the service life of turbine engines.

[0102] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0103] Unless otherwise specified, the relative arrangement of the parts and steps, numerical expressions and numerical values ​​set forth in these embodiments do not limit the scope of the present application. Meanwhile, it should be understood that, for ease of description, the sizes of the various parts shown in the accompanying drawings are not drawn according to actual proportional relationships. Technology, methods and equipment known to those of ordinary skill in the relevant art may not be discussed in detail, but in appropriate cases, the technology, methods and equipment should be considered as a part of the specification. In all examples shown and discussed here, any specific value should be interpreted as being merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments can have different values. It should be noted that similar numbers and letters represent similar items in the following drawings, and therefore, once an item is defined in an accompanying drawing, it does not need to be further discussed in subsequent drawings.

[0104] In the description of this application, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "horizontal, vertical, vertical, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of this application; the directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0105] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figures. For example, if the device in the drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0106] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of this application.

[0107] The above description is merely a preferred embodiment of the present application and is not intended to limit the present application. Various modifications and variations are possible for those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present application shall be included within the scope of protection of the present application.

Claims

1. A power transmission system, characterized in that: include: Turbine engine (10); a speed reduction mechanism (20), the turbine engine (10) being drivingly connected to at least a portion of the speed reduction mechanism (20), the speed reduction mechanism (20) being used to drive a first load to move; A power conversion mechanism (40) is provided between the speed reduction mechanism (20) and the first load, the power conversion mechanism (40) having a first power connection state for connecting the first load to the speed reduction mechanism (20) and a first power disconnection state for disconnecting the first load from the speed reduction mechanism (20).

2. The power transmission system according to claim 1, characterized in that: The power conversion mechanism (40) comprises: a first clutch (41), the first clutch (41) being used to disengage from or engage with the speed reduction mechanism (20); or, A first clutch (41) and a first brake (42); when the first clutch (41) is disengaged from the reduction mechanism (20), the first brake (42) is used to brake the power output part of the power conversion mechanism (40) or the power input part of the first load; when the first clutch (41) is engaged with the reduction mechanism (20), the first brake (42) releases the brake on the power output part of the power conversion mechanism (40) or the power input part of the first load.

3. The power transmission system according to claim 1, characterized in that: The speed reduction mechanism (20) comprises: A first reduction structure (21) and a second load (22), wherein the turbine engine (10) is drivingly connected to the first reduction structure (21), the first reduction structure (21) having a first power output end and a second power output end, the first power output end being drivingly connected to the first load, the second power output end being drivingly connected to the second load (22), and the first reduction structure (21) can be selectively drivingly connected to the first load and / or the second load (22).

4. The power transmission system according to claim 3, characterized in that: The second load (22) is a generator or a motor.

5. The power transmission system according to claim 3, characterized in that: The power transmission system further comprises: The speed regulating mechanism (30) comprises a second reduction gear structure (31) and a speed regulating motor (32), wherein the second reduction gear structure (31) has a first power input end and a second power input end, wherein the first power input end can be selectively connected to or disconnected from the first power output end, the power output part of the second reduction gear structure (31) is drivingly connected to the first load, the second power input end can be selectively connected to or disconnected from the power output part of the speed regulating motor (32), and the second load (22) is used to be selectively connected to the speed regulating motor (32) to supply power to the speed regulating motor (32).

6. The power transmission system according to claim 5, characterized in that: The speed regulating mechanism (30) further comprises: A switching mechanism (33) is provided between the second power input terminal and the speed regulating motor (32). The switching mechanism (33) has a second power connection state in which the second power input end is connected to the speed regulating motor (32) and a second power disconnection state in which the second power input end is disconnected from the speed regulating motor (32).

7. The power transmission system according to claim 6, characterized in that: The switching mechanism (33) comprises: A second clutch (331), the second clutch (331) being used to be disengaged from or engaged with the speed regulating motor (32); The second brake (332) is connected to the second clutch (331); when the second clutch (331) is disengaged from the speed regulating motor (32), the second brake (332) is used to brake the second power input end; when the second clutch (331) is engaged with the speed regulating motor (32), the second brake (332) releases the brake on the second power input end.

8. The power transmission system according to claim 5, characterized in that: The first deceleration structure (21) comprises: a first power input shaft (211), wherein the first power input shaft (211) forms a power input portion of the first reduction mechanism (21); A first planetary gear structure (212), wherein a power input portion of the first planetary gear structure (212) is connected to the power input shaft; A first power output shaft (213) connected to the power output portion of the first planetary gear structure (212), the first power output shaft (213) forming the first power output end; A first parallel gear set (214), wherein the first parallel gear set (214) is connected to the first power output shaft (213), and the power output portion of the first parallel gear set (214) forms the second power output end.

9. The power transmission system according to claim 8, characterized in that: The first planetary gear structure (212) comprises: A first sun gear (2121), a first planetary gear (2122), a first planetary carrier (2123) and a first ring gear (2124), wherein the first planetary gear (2122) is meshed with the first sun gear (2121), the first planetary gear (2122) is mounted on the first planetary carrier (2123), the first planetary carrier (2123) is fixedly arranged, the first planetary gear (2122) drives the first ring gear (2124) to rotate, and the first ring gear (2124) is connected to the first power output shaft (213).

10. The power transmission system according to claim 9, characterized in that: The first deceleration structure (21) further comprises: The starter motor (215) can be selectively connected to or disconnected from the first planetary gear (2122) so as to drive the first planetary gear (2122) to move or be disconnected from the first planetary gear (2122) through the starter motor (215).

11. The power transmission system according to claim 10, characterized in that: The first deceleration structure (21) further comprises: a second parallel gear set (216), the second parallel gear set (216) being arranged between the starter motor (215) and the first planetary gear (2122), the first power connection portion of the second parallel gear set (216) being connected to the starter motor (215), and the second power connection portion of the second parallel gear set (216) being connected to the first planetary gear (2122); a third clutch (217) disposed between the power input portion of the second parallel gear set (216) and the starter motor (215); When the rotation speed of the starter motor (215) is greater than the rotation speed of the first power connection part, the third clutch (217) is engaged so that the starter motor (215) drives the first power connection part to rotate; when the rotation speed of the starter motor (215) is less than the rotation speed of the first power connection part, the third clutch (217) is disengaged so that the starter motor (215) is disconnected from the first power connection part.

12. The power transmission system according to claim 11, characterized in that: The second deceleration structure (31) comprises: A second power input shaft (311) and a third power input shaft (312), wherein the second power input shaft (311) has the first power input end, and the third power input shaft (312) has the second power input end; a second planetary gear structure (313), wherein the second planetary gear structure (313) comprises a second sun gear (3131), a second planetary gear (3132), a second planet carrier (3133) and a second ring gear (3134), wherein the second planetary gear (3132) is meshed with the second sun gear (3131), the second planetary gear (3132) is mounted on the second planet carrier (3133), the second planet carrier (3133) and the second sun gear (3131) are connected to the second power input shaft (311), and the second ring gear (3134) is connected to the third power input shaft (312); The second power output shaft (314) is connected to the second planetary carrier (3133), and the second power output shaft (314) forms the power output part of the second reduction structure (31).

13. The power transmission system according to claim 12, characterized in that: The second deceleration structure (31) further comprises: A transmission gear (315), the third power input shaft (312) is connected to the transmission gear (315), and the transmission gear (315) is meshed with the second ring gear (3134), so that the third power input shaft (312) is connected to the second ring gear (3134) through the transmission gear (315).

14. The power transmission system according to any one of claims 5 to 13, characterized in that: The first load is a plunger pump (50); Wherein, the plunger pump (50) comprises a third parallel gear set (51) and a hydraulic end (53) connected to each other; the power output part of the second reduction gear structure (31) is connected to the power input part of the third parallel gear set (51); or, The plunger pump (50) comprises a third parallel gear set (51), a third planetary gear structure (52) and a hydraulic end (53) which are connected in sequence; the speed regulating mechanism (30) is arranged between the third parallel gear set (51) and the third planetary gear structure (52); the third parallel gear set (51) is arranged between the first power input end and the first power output end, so that the first power input end is connected to the first power output end through the third parallel gear set (51); the power output part of the second reduction structure (31) is connected to the power input part of the third planetary gear structure (52).

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