Power transmission system

Abstract

The application provides a power transmission system, comprising: a turbine engine; a reduction mechanism, the turbine engine being at least partially drivingly connected to the reduction mechanism, the reduction mechanism being configured to drive a first load; a power conversion mechanism being disposed between the reduction mechanism and the first load, the power conversion mechanism having a first power connection state in which the first load is connected to the reduction mechanism and a first power disconnection state in which the first load is disconnected from the reduction mechanism. The technical scheme provided by the application can solve the technical problem of short service life of a power turbine of a turbine engine in the prior art.

Description

Technical Field

[0001] This invention relates to the field of power system technology for fracturing equipment, and more specifically, to a power transmission system. Background Technology

[0002] Currently, with the development of fracturing equipment technology, fracturing equipment powered by turbine engines has emerged. Compared to traditional diesel engines, turbine engines offer many advantages, such as higher power density per unit, the ability to use 100% natural gas as fuel to reduce fuel costs, and more environmentally friendly emissions. Turbine engines have an idling mode, in which the compressor turbine rotates while the power turbine has no power output. To prevent the fracturing pump from being driven by the power turbine under no or very low load when the turbine engine is in idling mode, a brake is installed on the power output shaft of the high-speed planetary gearbox. This brake forces the power turbine to zero speed once the turbine engine is in idling mode.

[0003] However, in idle mode, the turbocharged engine's air compressor, combustion chamber, and compressor turbine are all running, and a large amount of hot air is still being discharged from the exhaust end. This hot air, after exiting the combustion chamber, first passes through the compressor turbine, driving it to rotate and subsequently powering the air compressor. Then, this hot air passes through the power turbine and is discharged to the exhaust end. During this process, because the power turbine is forcibly braked, it has to withstand the high temperature and pressure of the combustion gases as it passes through, which affects its lifespan and shortens its overall lifespan. Summary of the Invention

[0004] The main objective of this invention is to provide a power transmission system to solve the technical problem of the short service life of the power turbine in existing turbine engines.

[0005] To achieve the above objectives, the present invention provides a power transmission system, comprising:

[0006] Turbo engine;

[0007] A reduction gear mechanism, in which at least a portion of the turbine engine is driven to drive the first load to move;

[0008] A power conversion mechanism is disposed between a reduction gear and a first load. The power conversion mechanism has a first power connection state that connects the first load to the reduction gear and a first power disconnect state that separates the first load from the reduction gear.

[0009] Furthermore, the power conversion mechanism includes:

[0010] The first clutch is used to disengage or engage with the reduction gear; or...

[0011] A first clutch and a first brake; when the first clutch disengages from the reduction mechanism, the first brake is used to brake the power output section of the power conversion mechanism or the power input section of the first load; when the first clutch engages with the reduction mechanism, the first brake releases the braking of the power output section of the power conversion mechanism or the power input section of the first load.

[0012] Furthermore, the deceleration mechanism includes:

[0013] A first reduction structure and a second load are connected, and a turbine engine is driven 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 driven to the first load, and the second power output end is driven to the second load. The first reduction structure can be selectively driven to the first load and / or the second load.

[0014] Furthermore, the second load is a generator or an electric motor.

[0015] Furthermore, the powertrain system also includes:

[0016] The speed regulating mechanism includes a second reduction structure and a speed regulating motor. The second reduction 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 a first power output end. The power output part of the second reduction structure is driven and connected to a 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 connect to the speed regulating motor to supply power to the speed regulating motor.

[0017] Furthermore, the speed regulating mechanism also includes:

[0018] A switching mechanism is disposed between the second power input terminal and the speed regulating motor. The switching mechanism has a second power connection state that connects the second power input terminal to the speed regulating motor and a second power disconnection state that disconnects the second power input terminal from the speed regulating motor.

[0019] Furthermore, the switching mechanism includes:

[0020] The second clutch is used to disengage or engage with the speed-regulating motor.

[0021] The second brake is connected to the second clutch; when the second clutch disengages from the speed-regulating motor, the second brake is used to brake the second power input end; when the second clutch engages with the speed-regulating motor, the second brake releases the braking of the second power input end.

[0022] Furthermore, the first deceleration structure includes:

[0023] The first power input shaft forms the power input section of the first reduction structure;

[0024] The first planetary gear structure has a power input section connected to the power input shaft.

[0025] The first power output shaft is connected to the power output section of the first planetary gear structure, and the first power output shaft forms the first power output end;

[0026] 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.

[0027] Furthermore, the first planetary gear structure includes:

[0028] The system comprises a first sun gear, a first planet gear, a first planet carrier, and a first ring gear. The first planet gear meshes with the first sun gear and is mounted on the first planet carrier, which is fixedly positioned. The first planet gear drives the first ring gear to rotate and is connected to the first power output shaft.

[0029] Furthermore, the first deceleration structure also includes:

[0030] The starter motor can be selectively connected to or disconnected from the first planetary gear to drive the first planetary gear or disengage from it.

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

[0032] The second parallel gear set is disposed between the starter motor and the first planetary gear. The first power connection part of the second parallel gear set is connected to the starter motor, and the second power connection part of the second parallel gear set is connected to the first planetary gear.

[0033] The third clutch is located between the power input section of the second parallel gear set and the starter motor;

[0034] Specifically, when the speed of the starter motor is greater than the speed of the first power connection part, the third clutch engages to make the starter motor 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 make the starter motor disconnect from the first power connection part.

[0035] Furthermore, the second deceleration structure includes:

[0036] A second power input shaft and a third power input shaft, wherein the second power input shaft has a first power input end and the third power input shaft has a second power input end;

[0037] The second planetary gear structure includes a second sun gear, a second planet gear, a second planet carrier, and a second ring gear. The second planet gear meshes with the second sun gear and is mounted on the second planet carrier. The second sun gear on the second planet carrier is connected to the second power input shaft, and the second ring gear is connected to the third power input shaft.

[0038] The second power output shaft is connected to the second planetary carrier, and the second power output shaft forms the power output part of the second reduction structure.

[0039] Furthermore, the second deceleration structure also includes:

[0040] The transmission gear connects the third power input shaft to the transmission gear, which meshes with the second gear ring, so that the third power input shaft is connected to the second gear ring via the transmission gear.

[0041] Furthermore, the first load is a plunger pump, which includes a third parallel gear set, a third planetary gear structure, and a hydraulic drive structure connected in sequence.

[0042] In this configuration, the power output section of the second reduction gear structure is connected to the power input section of the third parallel gear set; or...

[0043] The speed regulating mechanism is located between the third parallel gear set and the third planetary gear structure. The third parallel gear set is located 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.

[0044] By applying the technical solution of this invention and setting a power conversion mechanism, the first load can have a first power state connected to the deceleration mechanism and a first power disconnection state that separates the first load from the deceleration mechanism. This facilitates the connection and transmission of power and avoids the power turbine being forcibly braked in the idling mode, which would cause the power turbine to be subjected to high temperature and pressure of the gas. This allows the power turbine to rotate naturally under the action of hot gas, thus avoiding the technical problem of a short service life of the power turbine caused by forced braking. Attached Figure Description

[0045] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0046] Figure 1 A schematic diagram of a power transmission system without a speed regulating mechanism according to an embodiment of the present invention is shown;

[0047] Figure 2 A schematic diagram of a power transmission system without a speed regulating mechanism according to another embodiment of the present invention is shown;

[0048] Figure 3 A schematic diagram of a power transmission system according to an embodiment of the present invention is shown;

[0049] Figure 4 A schematic diagram of the power conversion mechanism provided according to an embodiment of the present invention is shown;

[0050] Figure 5 A schematic diagram of the deceleration mechanism provided according to an embodiment of the present invention is shown;

[0051] Figure 6 A schematic diagram of the speed regulating mechanism provided according to an embodiment of the present invention is shown;

[0052] Figure 7 A schematic diagram of a plunger pump according to an embodiment of the present invention is shown;

[0053] Figure 8 A schematic diagram of a power transmission system according to another embodiment of the present invention is shown;

[0054] Figure 9 A schematic diagram of a plunger pump according to another embodiment of the present invention is shown.

[0055] The above figures include the following reference numerals:

[0056] 10. Turbine engine; 11. Compressor; 12. Combustion chamber; 13. Compressor turbine; 14. Power turbine;

[0057] 20. Reduction mechanism; 21. First reduction structure; 211. First power input shaft; 212. First planetary gear structure; 2121. First sun gear; 2122. First planet gear; 2123. First planet carrier; 2124. First gear ring; 213. First power output shaft; 214. First parallel gear set; 215. Starter motor; 216. Second parallel gear set; 217. Third clutch; 22. Second load;

[0058] 30. Speed ​​regulating mechanism; 31. Second 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 gear ring; 314. Second power output shaft; 315. Transmission gear; 32. Speed ​​regulating motor; 33. Switching mechanism; 331. Second clutch; 332. Second brake;

[0059] 40. Power conversion mechanism; 41. First clutch; 42. First brake;

[0060] 50. Piston pump; 51. Third parallel gear set; 52. Third planetary gear structure; 53. Hydraulic drive structure. Detailed Implementation

[0061] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0062] like Figures 1 to 9 As shown, an embodiment of the present invention provides a power transmission system including a turbine engine 10, a reduction gear 20, and a power conversion mechanism 40. The turbine engine 10 is at least partially driven connected to the reduction gear 20, which drives a first load. The power conversion mechanism 40 is disposed between the reduction gear 20 and the first load, and has a first power connection state connecting the first load to the reduction gear 20 and a first power disconnect state separating the first load from the reduction gear 20.

[0063] Using the power transmission system provided in this embodiment, the power conversion mechanism 40 enables the first load to have a first power state connected to the reduction mechanism 20 and a first power disconnection state to separate the first load from the reduction mechanism 20, which facilitates the connection and transmission of power. It also avoids the power turbine being forcibly braked in the idling mode, which would cause the power turbine to be subjected to high temperature and pressure of the gas. This allows the power turbine to rotate naturally under the action of hot gas, thus avoiding the technical problem of a short service life of the power turbine caused by forced braking.

[0064] 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 a first clutch 41 and a first brake 42; when the first clutch 41 disengages from the reduction mechanism 20, the first brake 42 brakes the power output section of the power conversion mechanism 40 or the power input section of the first load; when the first clutch 41 engages with the reduction mechanism 20, the first brake 42 releases the braking of the power output section of the power conversion mechanism 40 or the power input section of the first load. This structural arrangement facilitates effective disengagement while braking, preventing the braking of the turbine engine 10 from continuing to affect its operation. Specifically, when the turbine engine 10 is a dual-shaft turbine engine, when the dual-shaft turbine engine 10 is in idle mode, using braking while engaging the clutch, compared to simple braking, can effectively reduce the impact of braking on the power turbine on its service life.

[0065] The power conversion mechanism 40 operates by disengaging or engaging the power transmitted from the power input section of the power conversion mechanism 40 via the first clutch 41. The first brake 42 applies braking to the power output section of the power conversion mechanism 40 when the first clutch 41 is disengaged; and releases the braking to the power output section of the power conversion mechanism 40 when the first clutch 41 is engaged.

[0066] 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.

[0067] In this embodiment, the reduction mechanism 20 includes a first reduction structure 21 and a second load. The turbine engine 10 is driven and connected to the first reduction structure 21. The first reduction structure 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 structure 21 can be selectively driven and connected to the first load and / or the second load. Specifically, the first reduction structure 21 can be driven and connected to the first load; or, the first reduction structure 21 can be driven and connected to the second load; or, the first reduction structure 21 can be driven and connected to both the first load and the second load to drive the first load and the second load to work. This allows for flexible adjustment of the working conditions of the first load and the second load according to actual working conditions.

[0068] Specifically, the second load is a generator, an electric motor, or a starter generator.

[0069] In this embodiment, the power transmission system further includes a speed regulating mechanism 30, which includes a second reduction structure 31 and a speed regulating motor 32. The second reduction 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 a first power output end. The power output part of the second reduction structure 31 is connected to a first load drive, and the second power input end can be selectively connected to or disconnected from the power output part of the speed regulating motor 32. The second load 22 is used to connect to the speed regulating motor 32 to supply power to the speed regulating motor 32. By using the speed regulating mechanism 30 for speed regulation, it is not necessary to limit the turbine engine 10 to have a speed regulation function. Only the appropriate turbine engine 10 needs to be selected according to the required external dimensions and weight, thus increasing the selection range of the turbine engine 10.

[0070] In this embodiment, the powertrain system has three different operating modes: pure electric mode, pure engine mode, and hybrid mode. In pure electric mode, the generator is connected to the speed-regulating motor 32 to supply power to it. 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 section of the speed-regulating motor 32. In 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 section of the speed-regulating motor 32. In 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 section of the speed-regulating motor 32. This allows for easy selection of different modes to drive the components according to actual usage requirements.

[0071] Specifically, the turbine engine 10 here 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 regular generator or a starter generator integrated unit.

[0072] In this embodiment, the speed regulating mechanism 30 further includes a switching mechanism 33. The switching mechanism is disposed between the second power input terminal and the speed regulating motor 32. The switching mechanism 33 has a second power connection state that connects the second power input terminal to the speed regulating motor 32 and a second power disconnection state that disconnects the second power input terminal 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, enabling smooth switching and facilitating the switching of the power transmission system to different operating modes.

[0073] Specifically, the switching mechanism 33 includes a second clutch 331 and a second brake 332. The second clutch 331 is used to disengage from 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 brakes the second power input end. When the second clutch 331 is engaged with the speed-regulating motor 32, the second brake 332 releases the braking of the second power input end. This structural arrangement facilitates effective disengagement and engagement while braking, avoiding situations where braking affects the operating life of the speed-regulating motor 32, thereby improving the operating life of the speed-regulating motor 32.

[0074] In this embodiment, the first reduction 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 part of the first reduction structure 21, and the power input part 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 part 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 part of the first parallel gear set 214 forms a second power output end. This structural arrangement facilitates effective reduction operation and the formation of both the first and second power output ends, thereby facilitating effective power output switching.

[0075] Specifically, the first planetary gear structure 212 in this embodiment includes a first sun gear 2121, a first planet gear 2122, a first planet carrier 2123, and a first ring gear 2124. The first planet gear 2122 meshes with the first sun gear 2121, and is mounted on the first planet carrier 2123. The first planet carrier 2123 is fixedly installed. The first planet 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. This structural arrangement is simple and facilitates stable deceleration operation.

[0076] In this embodiment, the first reduction structure 21 further includes a starter motor 215, which 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 disengage from the first planetary gear 2122. This structural arrangement facilitates providing external starting assistance, ensuring stable starting of the first planetary gear 2122, and also facilitates disengagement 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.

[0077] Specifically, in this embodiment, the first reduction structure 21 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 rotational speed of the starter motor 215 is greater than the rotational speed of the first power connection portion, the clutch engages to cause the starter motor 215 to drive the first power connection portion to rotate; when the rotational speed of the starter motor 215 is less than the rotational speed of the first power connection portion, the clutch disengages to disengage the starter motor 215 from the first power connection portion. This structural design allows for an effective increase in the speed of the first planetary gear 2122 when its speed is low; after the first planetary gear 2122 has successfully started, it can smoothly separate from the starter motor 215, thus avoiding any impact of the starter motor 215 on the operation of the first planetary gear 2122.

[0078] Specifically, the working principle of the reduction mechanism 20 is as follows: power from upstream is input through the first power input shaft 211, driving the first sun gear 2121 to rotate. The first sun gear 2121 drives the first planetary gear 2122 to rotate. The first planetary carrier 2123 remains fixed. The first planetary gear 2122 drives the first gear ring 2124 to rotate. The first gear ring 2124 drives the first power output shaft 213 to rotate, thus realizing the output of the main force. In addition, the first power output shaft 213 also drives the generator or the starter-generator integrated unit to rotate through the first parallel gear set 214, thus realizing 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.

[0079] In this embodiment, the second reduction structure 31 includes a second power input shaft 311, a third power input shaft 312, a second planetary gear structure 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 structure 313 includes a second sun gear 3131, second planet gears 3132, a second planet carrier 3133, and a second ring gear 3134. The second planet gears 3132 mesh with the second sun gear 3131 and are mounted on the second planet carrier 3133. The second sun gear 3131 is 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 planet carrier 3133 and forms the power output part of the second reduction structure 31. This structural design facilitates the optimization of the power input and output layout of the second deceleration structure 31, thereby enabling the optimization of the deceleration structure and achieving deceleration and speed regulation effects.

[0080] Specifically, the second reduction structure 31 also includes a transmission gear 315, and the third power input shaft 312 is connected to the transmission gear 315. The transmission gear 315 meshes with the second gear ring 3134, so that the third power input shaft 312 is connected to the second gear ring 3134 through the transmission gear 315. Specifically, the transmission gear 315 meshes with the external teeth of the second gear ring 3134 to facilitate the smooth driving of the second gear ring 3134 through the transmission gear 315, thereby facilitating smooth speed adjustment and effectively achieving the speed adjustment effect.

[0081] The working principle of the speed regulating mechanism 30 is as follows: power from upstream is input through the second power input shaft 311, which drives the second sun gear 3131 to rotate. The second sun gear 3131 drives the second planet gear 3132 to rotate, which in turn drives the second planet carrier 3133 to rotate. The second planet carrier 3133 also drives the second power output shaft 314 to rotate. Additionally, the rotational speed of the second ring gear 3134 is driven by the speed regulating motor 32. Based on the single-row planetary gear set equation: nsun + αnannulus - (1 + α)ncarrier = 0, where nsun is the sun gear speed; nannulus is the ring gear speed; ncarrier is the planet carrier speed; and α is the ratio of the number of teeth on the ring gear (zannulus) to the number of teeth on the sun gear (zsun), i.e., α = zannulus / zsun, and α > 1. Therefore, the rotational speed of the planet carrier 3, ncarrier = (nsun + αnannulus) / (1 + α). Based on the above formula, when the speed-regulating motor 32 has no output speed, the second clutch 331 will disengage from the power input of the speed-regulating motor 32, and the second brake 332 will brake the second ring gear 3134, meaning that the speed of the second ring gear 3134 is 0. At this time, the speed of the second planetary carrier 3133 is ncarrier = nsun / (1+α), which means that the output speed of the speed-regulating planetary gearbox is determined only by the speed ratio α of the second ring gear 3134 and the second sun gear 3131. When the speed-regulating motor 32 is running, the second clutch 331 will engage the power input of the speed-regulating motor 32, and the second brake 332 will disengage the brake on the second ring gear 3134. Thus, the speed-regulating motor 32 drives 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, which is also the highest rotational speed of the corresponding second gear ring 3134, the rotational speed of the planetary carrier, which is also the output speed of the speed regulating gearbox, reaches its maximum.

[0082] In this embodiment, the power transmission system further includes a plunger pump 50, which forms the driven component. The plunger pump 50 includes a third parallel gear set 51, a third planetary gear structure 52, and a hydraulic drive structure 53 connected in sequence.

[0083] Specifically, the main working principle of the plunger pump 50 is as follows: power from upstream is input into the power input section of the plunger pump 50, and is reduced in speed by the third parallel gear set 51 and the third planetary gear structure 52, driving the crankshaft in the power output section of the plunger pump 50 to rotate, thereby driving the plunger to run. The hydraulic drive structure 53 completes the functions of low-pressure suction and high-pressure pumping.

[0084] Among them, such as Figure 1 and Figure 2As shown, the power transmission system in this embodiment does not include the speed regulating mechanism 30. The first reduction structure 21 can be a high-speed reduction gearbox, with a power take-off port installed on the high-speed reduction gearbox to drive the load, and a clutch 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 in idle mode without the need for forced braking of the power turbine, thus avoiding overspeed and potential impact on the lifespan of the turbine engine.

[0085] Figure 1 The power transmission system and Figure 2 The difference in the power transmission system lies in the specific arrangement of the power conversion mechanism 40. For example... Figure 1 As shown, the first clutch 41 and the first brake 42 can be combined into one component, installed between the power output end of the high-speed reduction gearbox and the power input end of the fracturing plunger pump. Figure 2 As shown, the first clutch 41 is positioned between the power output end of the high-speed reduction gearbox and the power input end of the fracturing plunger pump. The first brake 42 is spaced apart from the first clutch 41 and 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 via 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 when the first clutch 41 is engaged.

[0086] The high-speed gearbox works as follows: power from upstream is input through the power input shaft, driving the sun gear to rotate. The sun gear drives the planetary gears to rotate, while the planet carrier remains fixed. The planetary gears drive the ring gear to rotate, and the ring gear drives the power output shaft to achieve the output of main power. Additionally, the power output shaft also drives a generator or an integrated generator / starter unit via parallel gears to achieve the power generation function.

[0087] The main working process of this powertrain system is described as follows:

[0088] Normal operation of the fracturing plunger pump: In normal operation mode, the power output of the turbine engine 10 is reduced in speed and increased in torque through a high-speed reduction gearbox. This power drives the second load 22 and, via the drive shaft and the first clutch 41, the fracturing plunger pump. At this time, the first clutch 41 is engaged. The first brake 42 is in a non-braking state.

[0089] Turbine engine idle mode: In idle mode, turbine engine 10 is in idle mode, second load 22 is in working state, first clutch 41 is in disengaged state, and first brake 42 is in braking state.

[0090] Turbine engine shutdown mode: When the turbine engine is in shutdown mode, the first brake 42 is in a non-braking state to facilitate the operator's maintenance of the fracturing plunger pump.

[0091] like Figures 3 to 7 As shown, in one embodiment, the power output section of the second deceleration structure 31 is connected to the power input section 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.

[0092] In this embodiment, the corresponding power transmission system operates as follows: the power output from the gas turbine engine 10 is reduced in speed and increased in torque by a high-speed reduction gearbox (corresponding to reduction mechanism 20), then further reduced in speed and increased in torque by a power converter and a speed-regulating planetary reduction gearbox (corresponding to speed-regulating mechanism 30), driving the fracturing plunger pump 50 to operate. The specific operating modes of this power transmission system are as follows:

[0093] 1) Pure Electric Mode – The operating mode of the fracturing pump directly driven by a pure electric motor. 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 speed-regulating planetary 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 gearbox. In this mode, the gas turbine engine 10 can drive the high-speed gearbox, which, due to the generator mounted on it, can generate electricity. Additionally, in this mode, the first clutch 41 mounted on the speed-regulating planetary gearbox engages, and the second brake 332 disengages the second ring gear 3134. The motor can then drive the second planetary gear 3132 by rotating the second ring gear 3134, and power is output from the second power output shaft 314 via the second planetary carrier 3133 to drive the fracturing pump. In this operating mode, the flow rate of the fracturing pump can be adjusted by the motor speed control. The generator mounted on the high-speed gearbox can supply power to the motor mounted on the speed-regulating planetary gearbox.

[0094] 2) Pure Engine Mode – The operating mode of the pure turbine engine 10 directly drives the fracturing pump. In this mode, the first clutch 41 of the power converter engages, and the first brake 42 disengages. The motor on the speed-regulating planetary gearbox stops running, the second clutch 331 disengages, and the second brake 332 brakes the second gear ring 3134. The output power of the gas turbine engine 10 directly drives the fracturing plunger pump 50 through the high-speed gearbox and the speed-regulating planetary gearbox.

[0095] 3) Hybrid Mode – Turbocharged Direct Drive + Motor Speed ​​Regulation Hybrid Mode. This mode is based on the turbocharged direct drive operation mode with the motor speed regulation mode activated. Specifically, the first clutch 41 of the power converter engages, and the first brake 42 disengages. The second clutch 331 on the speed regulation planetary gearbox engages, the second brake 332 disengages from the second ring gear 3134, and the speed regulation motor 32 rotates, thereby driving the second ring gear 3134. Based on the single-row planetary gear equation of the planetary gearbox, the rotational speed n of the second planetary carrier 3133 in this mode is... carrier =(n sun +αn annulus When the speed of the speed-regulating motor 32 is at its highest, which corresponds to the highest speed of the second gear ring 3134, the speed of the second planetary carrier 3133, which is the output speed of the speed-regulating reducer, reaches its maximum.

[0096] like Figure 8 and Figure 9 As shown, 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, 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. Alternatively, the speed regulating mechanism 30 and the plunger pump 50 can be understood as an integrated structure, which facilitates integrated installation and operation, simplifying the operator's process.

[0097] In this embodiment, the main working principle is as follows: Power from upstream is input through the power input section 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 reducer, the power is output from the third planetary carrier of the third planetary gear structure 52. The power then drives 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 gears. Since the third gear ring of the third planetary gear structure 52 is fixed, the power is output from the third power output shaft through the third planetary carrier, driving the crankshaft of the fracturing plunger pump 50 to rotate. 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.

[0098] In summary, the working process of this power transmission system is as follows: the power output from the gas turbine engine 10 is reduced in speed and increased in torque by a high-speed reduction gearbox (reduction mechanism 20), and then driven by a 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 operating modes of this power transmission system are as follows:

[0099] 1) Pure Electric Mode – The operating mode of the fracturing pump directly driven by a pure electric motor. 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 drive gear inside the third parallel gear set 51 of the fracturing plunger pump 50, thereby braking the second sun gear 3131 of the speed regulating mechanism 30. In this mode, the gas turbine engine 10 can drive the high-speed reduction gearbox, and since a generator is installed on the high-speed reduction gearbox, this mode can 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 brake on the second ring gear 3134 on the second planetary gear structure 313. The motor can drive the second ring gear 3134 to rotate, thereby driving the second planetary gear 3132. Due to the braking of the second sun gear 3131, power is output from the second power output shaft 314 through 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 then the power drives the fracturing pump crankshaft through the third planetary carrier and the third power output shaft of the third planetary gear structure 52. In this operating mode, the flow rate of the fracturing pump can be adjusted by the speed regulating motor 32. The generator mounted on the reduction mechanism 20 can supply power to the speed regulating motor 32 mounted on the second reduction structure 31.

[0100] 2) Pure Engine Mode – The operating mode of the pure turbine engine 10 directly drives the fracturing pump. In this mode, the second clutch 331 of the power converter engages, and the second brake 332 disengages. The motor on the second reduction gear 31 stops operating, the second clutch 331 disengages, and the second brake 332 brakes the second gear ring 3134. The second sun gear 3131 of the second reduction gear 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 after passing through the high-speed reduction gearbox and the power converter. In this operating mode, the second gear ring 3134 of the second reduction gear 31 is in a braking state and has no speed regulation function.

[0101] 3) Hybrid Mode – Turbine Direct Drive + Motor Speed ​​Regulation Hybrid Mode. This mode is based on the turbine direct drive working mode described above, but with the motor speed regulation mode activated. Specifically, the first clutch 41 of the power converter engages, and the first brake 42 disengages. The second clutch 331 on the speed regulation mechanism 30 engages, and the second brake 332 disengages from the second ring gear 3134. The speed regulation motor 32 operates, thereby driving the ring gear. Based on the single-row planetary gear equation of the planetary gearbox, in this mode, the rotational speed of the second planetary carrier 3133 is ncarrier = (nsun + αnannulus) / (1 + α). When the speed regulation motor 32 reaches its highest speed, which corresponds to the highest speed of the second ring gear 3134, the rotational speed of the second planetary carrier 3133, which is also the rotational speed of the second power output shaft 314 of the second reduction structure 31, reaches its maximum.

[0102] As can be seen from the above description, the embodiments of the present invention achieve the following technical effects: expanding the selection range of turbine engines and increasing the service life of turbine engines.

[0103] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0104] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0105] In the description of this application, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is usually based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this application; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0106] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0107] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0108] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A power transmission system, characterized in that, include: Turbine engine (10); A reduction mechanism (20) is provided, wherein at least a portion of the turbine engine (10) is driven to the reduction mechanism (20), the reduction mechanism (20) is used to drive the movement of a first load, and includes a first reduction structure (21) and a second load (22), wherein the turbine engine (10) is driven to the first reduction structure (21), the first reduction structure (21) has a first power output end and a second power output end, the first power output end is driven to the first load, the second power output end is driven to the second load (22), and the first reduction structure (21) may be selectively driven to the first load and / or the second load (22); A power conversion mechanism (40) is disposed between the reduction mechanism (20) and the first load. The power conversion mechanism (40) has a first power connection state that connects the first load to the reduction mechanism (20) and a first power disconnect state that separates the first load from the reduction mechanism (20). The speed regulating mechanism (30) includes a second reduction structure (31) and a speed regulating motor (32). The second reduction 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 part of the second reduction structure (31) is driven and 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). The second load (22) is a generator, a motor, or a generator-starter integrated machine. When the second load (22) is used for power generation, the second load (22) is connected to the speed regulating motor (32) to supply power to the speed regulating motor (32).

2. The power transmission system according to claim 1, characterized in that, The power conversion mechanism (40) includes: A first clutch (41) is used to disengage from or engage with the reduction mechanism (20); or, A first clutch (41) and a first brake (42); when the first clutch (41) disengages from the deceleration mechanism (20), the first brake (42) brakes the power output of the power conversion mechanism (40) or the power input of the first load; when the first clutch (41) engages with the deceleration mechanism (20), the first brake (42) releases the braking of the power output of the power conversion mechanism (40) or the power input of the first load.

3. The power transmission system according to claim 1, characterized in that, The second load (22) is a generator or an electric motor.

4. The power transmission system according to claim 1, characterized in that, The speed regulating mechanism (30) also includes: A switching mechanism (33) is disposed between the second power input end and the speed regulating motor (32). The switching mechanism (33) has a second power connection state that connects the second power input end to the speed regulating motor (32) and a second power disconnection state that disconnects the second power input end from the speed regulating motor (32).

5. The power transmission system according to claim 4, characterized in that, The switching mechanism (33) includes: 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) disengages from the speed regulating motor (32), the second brake (332) is used to brake the second power input end; when the second clutch (331) engages with the speed regulating motor (32), the second brake (332) releases the braking of the second power input end.

6. The power transmission system according to claim 1, characterized in that, The first deceleration structure (21) includes: The first power input shaft (211) forms the power input part of the first reduction structure (21); The first planetary gear structure (212) has a power input section connected to the power input shaft; The first power output shaft (213) is connected to the power output part of the first planetary gear structure (212), and the first power output shaft (213) forms the first power output end; The first parallel gear set (214) is connected to the first power output shaft (213), and the power output part of the first parallel gear set (214) forms the second power output end.

7. The power transmission system according to claim 6, characterized in that, The first planetary gear structure (212) includes: The system comprises a first sun gear (2121), a first planet gear (2122), a first planet carrier (2123), and a first ring gear (2124). The first planet gear (2122) meshes with the first sun gear (2121). The first planet gear (2122) is mounted on the first planet carrier (2123), which is fixedly installed. The first planet gear (2122) drives the first ring gear (2124) to rotate. The first ring gear (2124) is connected to the first power output shaft (213).

8. The power transmission system according to claim 7, characterized in that, The first deceleration structure (21) further includes: A starter motor (215) is selectively connected to or disconnected from the first planetary gear (2122) to drive the first planetary gear (2122) to move or to disengage from the first planetary gear (2122) via the starter motor (215).

9. The power transmission system according to claim 8, characterized in that, The first deceleration structure (21) further includes: The second parallel gear set (216) is disposed between the starter motor (215) and the first planetary gear (2122). The first power connection part of the second parallel gear set (216) is connected to the starter motor (215), and the second power connection part 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 section of the second parallel gear set (216) and the starter motor (215); When the rotational speed of the starter motor (215) is greater than the rotational speed of the first power connection part, the third clutch (217) engages to make the starter motor (215) drive the first power connection part to rotate; when the rotational speed of the starter motor (215) is less than the rotational speed of the first power connection part, the third clutch (217) disengages to make the starter motor (215) disengage from the first power connection part.

10. The power transmission system according to claim 9, characterized in that, The second deceleration structure (31) includes: 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; The second planetary gear structure (313) includes a second sun gear (3131), a second planet gear (3132), a second planet carrier (3133), and a second ring gear (3134). The second planet gear (3132) meshes with the second sun gear (3131). The second planet gear (3132) is mounted on the second planet carrier (3133). The second sun gear (3131) is connected to the second power input shaft (311). 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).

11. The power transmission system according to claim 10, characterized in that, The second deceleration structure (31) also includes: The transmission gear (315) is connected to the third power input shaft (312), and the transmission gear (315) meshes with the second gear ring (3134) so ​​that the third power input shaft (312) is connected to the second gear ring (3134) through the transmission gear (315).

12. The power transmission system according to any one of claims 1 to 11, characterized in that, The first load is a plunger pump (50), which includes a third parallel gear set (51), a third planetary gear structure (52), and a hydraulic drive structure (53) connected in sequence. In this configuration, the power output section of the second reduction structure (31) is connected to the power input section of the third parallel gear set (51); or, 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, 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 deceleration structure (31) is connected to the power input part of the third planetary gear structure (52).

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