Fracturing pump power end and fracturing pump comprising same

Abstract

The invention discloses a fracturing pump power end and a fracturing pump comprising the fracturing pump power end, the fracturing pump power end comprises a box body, the box body is communicated with an input channel, and a first crankshaft and a second crankshaft which are distributed on the two opposite sides of the input channel are arranged in the box body; the transmission mechanism is arranged in the input channel and comprises a first-stage transmission mechanism and a second-stage transmission mechanism which are in transmission connection, the free end of the first-stage transmission mechanism is in transmission connection with an engine, and the free end of the second-stage transmission mechanism is in transmission connection with the engine. And the free end of the second-stage transmission mechanism is in transmission connection with the first crankshaft and the second crankshaft. According to the fracturing pump power end and the fracturing pump comprising the fracturing pump power end, speed reduction is achieved in a two-stage transmission mode, the diameter of a speed reduction large gear of the power end is reduced, so that the maximum boundary dimension of the power end is reduced, the length and height of the fracturing pump are minimized, the stroke of the fracturing pump is maximized, the stroke frequency of the fracturing pump is minimized, and the service life of quick-wear parts of the fracturing pump is prolonged.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of power systems, and more particularly to a fracturing pump power end and a fracturing pump comprising the same. BACKGROUND

[0002] The fracturing pump is installed on a vehicle chassis to form a fracturing vehicle. The power generated by the engine on the vehicle platform is transmitted to the fracturing pump power end through the hydraulic transmission box and the transmission shaft, and then the reciprocating motion of the piston or plunger in the pump cylinder is driven by the crankshaft rotation through the crosshead. Meanwhile, the fracturing fluid supplied by the sand mixing vehicle enters the fracturing pump through the low-pressure manifold, and is discharged by the high-pressure discharge pipe after being pressurized by the fracturing pump, thereby completing the downhole fracturing operation under the alternating action of suction and discharge.

[0003] At present, the market demand for fracturing pump wear parts is longer and longer, that is, in a certain working period, the wear parts should be replaced as few as possible to improve the fracturing efficiency, expand the fracturing income and reduce the operation and maintenance cost. In order to prolong the service life of the fracturing pump wear parts, the stroke is increased and the stroke frequency is reduced under the condition that the power of the fracturing pump is unchanged or is designed to be larger. For example, the stroke of the fracturing pump has been developed from 6 inches and 8 inches in the early stage to 10 inches and 11 inches at present. Since the overall width of the fracturing vehicle cannot exceed 2500 mm, the width of the fracturing pump cannot exceed 2500 mm. The stroke frequency can be reduced by increasing the gear ratio of the gear pair in the reduction mechanism. The speed ratio of the fracturing pump has been developed from 4.62, 6.353 and 6.873 in the early stage to 7.95, and even the planned speed ratio is greater than 8. Correspondingly, the stroke frequency has been reduced from 450 strokes per minute in the early stage to 230 strokes per minute at present. Under the limitation of the maximum width of the fracturing pump of 2500 mm, increasing the gear ratio of the gear pair will significantly increase the outer diameter of the large gear of the one-stage transmission gear pair, and thus greatly increase the maximum external dimensions of the fracturing pump, which is not conducive to the realization of the large stroke design of the fracturing pump.

[0004] Therefore, there is a need for a fracturing pump power end and a fracturing pump comprising the same to solve the above problems. SUMMARY

[0005] In view of the above, the purpose of the present application is to provide a fracturing pump power end and a fracturing pump comprising the same to solve the problem of minimizing the length and height of the fracturing pump when the stroke, stroke frequency and width of the fracturing pump are mutually restricted.

[0006] Based on the above purpose, the present application provides a fracturing pump power end, comprising:

[0007] a box body, an input channel being communicated on the box body, a first crankshaft and a second crankshaft being arranged in the box body and distributed on opposite sides of the input channel;

[0008] A transmission mechanism is disposed within the input channel. The transmission mechanism includes a first-stage transmission mechanism and a second-stage transmission mechanism that are connected in a transmission connection. The free end of the first-stage transmission mechanism is connected in a transmission connection to the engine, and the free end of the second-stage transmission mechanism is connected in a transmission connection to the first crankshaft and the second crankshaft.

[0009] Preferably, the housing includes a gearbox and a first crankshaft housing and a second crankshaft housing respectively connected to opposite sides of the gearbox. A first guide housing and a second guide housing are respectively connected to the first crankshaft housing and the second crankshaft housing. The input channel is disposed on the gearbox. The first crankshaft and the second crankshaft are respectively disposed in the first crankshaft housing and the second crankshaft housing. At least two opposing connecting rod assemblies are disposed on the first crankshaft and the second crankshaft housing. The connecting rod assemblies on the first crankshaft can reciprocate through the first crankshaft housing and the first guide housing. The connecting rod assemblies on the second crankshaft can reciprocate through the second crankshaft housing and the second guide housing.

[0010] Preferably, the first crankcase and / or the second crankcase are detachably connected to the gearbox.

[0011] Preferably, the first-stage transmission mechanism includes an input gear shaft and a herringbone gear shaft assembly that are meshed together. The input gear shaft passes through the input channel and is rotatably connected. The herringbone gear shaft assembly is disposed within the input channel and is rotatably connected. The free end of the input gear shaft is connected to the engine for transmission. The free end of the herringbone gear shaft assembly is connected to the second-stage transmission mechanism for transmission.

[0012] Preferably, the herringbone gear shaft assembly includes an interference-fit herringbone gear shaft and a first gear, the herringbone gear shaft being connected to the second-stage transmission mechanism, and the first gear being meshed with the input gear shaft.

[0013] Preferably, a first mounting hole is provided on each of the opposite sides of the input channel, and a first cylindrical roller bearing and a first tapered bearing are respectively provided in the two first mounting holes, with the input gear shaft passing through and connected to the first cylindrical roller bearing and the first tapered bearing in sequence; and / or a second mounting hole is provided on each of the opposite sides of the input channel, and a second cylindrical roller bearing and a second tapered bearing are respectively provided in the two second mounting holes, with the herringbone gear shaft passing through and connected to the second cylindrical roller bearing and the second tapered bearing in sequence.

[0014] Preferably, the second-stage transmission mechanism includes a herringbone gear assembly, which is disposed in the gearbox and rotatably connected. The input end of the herringbone gear assembly is meshed with the herringbone gear shaft, and the output end of the herringbone gear assembly is provided with a spline sleeve. Both the first crankshaft and the second crankshaft are connected to the spline sleeve via splines.

[0015] Preferably, both the first crankcase and the second crankcase are provided with bearing seats at the end facing the gearbox, and cylindrical roller bearings are provided on both bearing seats. The two cylindrical roller bearings pass through the opposite sides of the herringbone gear assembly.

[0016] In addition, preferably, the herringbone gear assembly includes a herringbone gear hub and a herringbone left-hand gear and a herringbone right-hand gear respectively sleeved on opposite sides of the herringbone gear hub, the herringbone gear hub is provided with mounting holes, and the spline sleeve is disposed in the mounting holes.

[0017] The present invention also proposes a fracturing pump, which includes the fracturing pump power end as described above.

[0018] As can be seen from the above, the fracturing pump power end and the fracturing pump including the present invention have the following advantages compared with the prior art: the fracturing pump power end adopts a two-stage transmission method to achieve deceleration. Under the same or greater speed ratio, the diameter of the large gear of the power end reduction is reduced to reduce the maximum external size of the power end, thereby minimizing the length and height of the fracturing pump, maximizing the stroke of the fracturing pump and minimizing the number of strokes, thereby improving the service life of the fracturing pump's vulnerable parts. Attached Figure Description

[0019] The above features and technical advantages of the present invention will become clearer and easier to understand from the following description of its embodiments in conjunction with the accompanying drawings.

[0020] Figure 1 This is a schematic diagram of the power end of the fracturing pump used in a specific embodiment of the present invention.

[0021] Figure 2 for Figure 1 The diagram shows the transmission state of the power end of the fracturing pump.

[0022] Figure 3 for Figure 2 The diagram shows the exploded view of the transmission state of the power end of the fracturing pump.

[0023] Figure 4 for Figure 3 An exploded side view of the transmission state of the power end of the fracturing pump, as shown.

[0024] Figure 5 for Figure 2The diagram shows a cross-sectional view of the transmission state of the power end of the fracturing pump.

[0025] Figure 6 for Figure 2 The diagram shows a herringbone gear shaft assembly at the power end of a fracturing pump.

[0026] Figure 7 for Figure 6 The diagram shows a cross-sectional view of the herringbone gear shaft assembly at the power end of the fracturing pump.

[0027] Figure 8 for Figure 2 The diagram shows a herringbone gear assembly at the power end of a fracturing pump.

[0028] Figure 9 for Figure 2 The diagram shows a splined sleeve on the power end of a fracturing pump.

[0029] The attached figures are labeled as follows:

[0030] 1. Hydraulic end clamping nut; 2. Connecting rod; 3. Hole retaining ring; 4. Axial oil seal; 5. Oil seal mounting base; 6. Socket head screw; 7. Fabric-reinforced oil-resistant gasket; 8. First guide housing; 9. Pin; 10. First screw; 11. Second screw; 12. Gearbox cover; 13. Input gear shaft; 14. Herringbone gear shaft assembly; 141. First gear; 142. Herringbone gear shaft; 15. Second cylindrical roller bearing; 16. Second shaft retaining ring; 17. First crankshaft housing; 18. Bearing housing; 19. Cylindrical roller bearing; 20. First crankshaft; 21. Herringbone gear assembly; 211. Nut; 212. First anti-loosening gasket; 213. Left-hand herringbone gear; 214. Herringbone gear hub; 215. Right-hand herringbone gear; 216. Cylindrical pin; 217. Screw; 22. Spline sleeve; 221. First external spline; 222. First internal spline; 223. Retaining ring groove; 23. First tapered bearing; 24. First retaining washer; 25. Locking nut; 26. End cover; 27. First bolt; 28. Input gear shaft cover; 29. ​​Second bolt; 30. Lip seal; 31. Second crankshaft housing; 32. Crankshaft bearing cover; 33. Third bolt; 34. Second lip seal; 35. Second crankshaft; 36. Crosshead and connecting rod assembly; 37. Second guide housing; 38. Fourth bolt; 39. Shaft retaining ring; 40. Bearing cap; 41. Second anti-loosening washer; 42. Fifth bolt; 43. Second tapered bearing; 44. First shaft retaining ring; 45. First cylindrical roller bearing; 46. Housing. Detailed Implementation

[0031] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to specific embodiments and the accompanying drawings. Identical components are denoted by the same reference numerals. It should be noted that the terms "front," "rear," "left," "right," "up," and "down" used in the following description refer to directions in the accompanying drawings. The terms "inner" and "outer" refer to directions toward or away from the geometric center of a specific component, respectively.

[0032] Figure 1 This is a schematic diagram of the power end of the fracturing pump used in a specific embodiment of the present invention. Figure 2 for Figure 1 The diagram shows the transmission state of the power end of the fracturing pump. Figure 3 for Figure 2 The diagram shows the exploded view of the transmission state of the power end of the fracturing pump. Figure 4 for Figure 3 An exploded side view of the transmission state of the power end of the fracturing pump, as shown. Figure 5 for Figure 2 The diagram shows a cross-sectional view of the transmission configuration of the power end of the fracturing pump. (See attached image.) Figures 1 to 5 As shown, the power end of the fracturing pump includes a housing 46 and a transmission mechanism.

[0033] The housing 46 is connected to an input channel, and the housing contains a first crankshaft 20 and a second crankshaft 35 distributed on opposite sides of the input channel.

[0034] The transmission mechanism is located in the input channel. The transmission mechanism includes a first-stage transmission mechanism and a second-stage transmission mechanism that are connected by transmission. The free end of the first-stage transmission mechanism is connected to the engine, and the free end of the second-stage transmission mechanism is connected to the first crankshaft 20 and the second crankshaft 35.

[0035] The driving force provided by the engine is transmitted to the first crankshaft 20 and the second crankshaft 35 through the transmission mechanism so as to drive the first crankshaft 20 and the second crankshaft 35 to rotate synchronously; specifically, the engine drives the first-stage transmission mechanism to rotate, the first-stage transmission mechanism drives the second-stage transmission mechanism to rotate, and the second-stage transmission mechanism drives the first crankshaft 20 and the second crankshaft 35 to rotate synchronously.

[0036] The power end of the fracturing pump adopts a two-stage transmission method to achieve deceleration. Under the same or greater speed ratio, the diameter of the large gear of the power end reduction is reduced to reduce the maximum external size of the power end, thereby minimizing the length and height of the fracturing pump, maximizing the stroke of the fracturing pump and minimizing the number of strokes, and thus improving the service life of the fracturing pump's vulnerable parts.

[0037] Preferably, the housing 46 includes a gearbox and a first crankshaft 20 housing 17 and a second crankshaft 35 housing 31 respectively connected to opposite sides of the gearbox. A first guide housing 8 and a second guide housing 37 are respectively connected to the first crankshaft 20 housing 17 and the second crankshaft 35 housing 31. An input channel is provided on the gearbox. The first crankshaft 20 and the second crankshaft 35 are respectively disposed in the first crankshaft 20 housing 17 and the second crankshaft 35 housing 31. At least two opposing connecting rod assemblies are provided on both the first crankshaft 20 and the crankshaft. The connecting rod assembly on the first crankshaft 20 can reciprocate through the first crankshaft 20 housing 17 and the first guide housing 8. The connecting rod assembly on the second crankshaft 35 can reciprocate through the second crankshaft 35 housing 31 and the second guide housing 37.

[0038] The first crankshaft 20 housing 17 and the second crankshaft 35 housing 31 are respectively located on opposite sides of the gearbox housing, while the first guide housing 8 and the second guide housing 37 are respectively located on the same side of the first crankshaft 20 housing 17 and the second crankshaft 35 housing 31. This allows for greater spatial freedom in the transmission mechanism, does not affect the overall length of the fracturing pump, facilitates overall machine design, and reduces space requirements. Furthermore, multiple connecting rod assemblies can be installed on the first crankshaft 20 and the second crankshaft 35, enabling a modular design of the fracturing pump and reducing costs.

[0039] In this embodiment, a first crankshaft 20 and a second crankshaft 35 are disposed within the gearbox housing, respectively located in the first crankshaft 20 housing 17 and the second crankshaft 35 housing 31 on opposite sides of the gearbox housing. The hydraulic end is also divided into two corresponding parts, corresponding to the first crankshaft 20 and the second crankshaft 35 respectively. The first crankshaft 20 housing 17 and the second crankshaft 35 housing 31 may adopt the same structure or different structures. The first guide housing 8 and the second guide housing 37 may adopt the same structure or different structures, such as both adopting crosshead guide housings. The first guide housing 8 cooperates with the first crankshaft 20 housing 17, and the second guide housing 37 cooperates with the second crankshaft 35 housing 31.

[0040] Two to four connecting rod assemblies are respectively provided on the first crankshaft 20 and the second crankshaft 35. Taking the first crankshaft 20 as an example, the housing 17 and the first guide housing 8 of the first crankshaft 20 can be configured as 2 cylinders, 3 cylinders or 4 cylinders. The hydraulic end corresponding to the first crankshaft 20 can also be configured as 2 cylinders, 3 cylinders or 4 cylinders. If the number of cylinders needs to be increased, it can be achieved by combining cylinders on both sides. If a 5-cylinder fracturing pump power end is required, 2 cylinders and 3 cylinders can be set on each side. If a 6-cylinder fracturing pump power end is required, 3 cylinders and 3 cylinders can be set on each side, and so on.

[0041] Preferably, the first crankshaft 20 housing 17 and / or the second crankshaft 35 housing 31 are detachably connected to the gearbox housing. By providing a detachable connection, the first crankshaft 20 housing 17 and / or the second crankshaft 35 housing 31 with different numbers of cylinders can be replaced, providing different combinations of cylinders and enabling modular production.

[0042] In this embodiment, the first crankshaft 20 housing 17 and / or the second crankshaft 35 housing 31 can be connected to the gearbox housing via flanges; the first guide housing 8 and the first crankshaft 20 housing 17 can be connected via screws, and the second guide housing 37 and the second crankshaft 35 housing 31 can be connected via screws.

[0043] In this embodiment, the gearbox is shaped like the number "9", the first crankshaft 20 housing 17 and the second crankshaft 35 housing 31 are hollow cylindrical, and the first guide housing 8 and the second guide housing 37 are hollow square.

[0044] Figure 6 for Figure 2 The diagram shows the herringbone gear shaft 142 assembly 14 at the power end of the fracturing pump. Figure 7 for Figure 6 A cross-sectional view of the herringbone gear shaft 142 assembly 14 at the power end of the fracturing pump, as shown. Figure 6 and Figure 7 As shown, the first-stage transmission mechanism includes an input gear shaft 13 and a herringbone gear shaft 142 assembly 14.

[0045] Preferably, the first-stage transmission mechanism includes an input gear shaft 13 and a herringbone gear shaft 142 assembly 14 that are meshed together. The input gear shaft 13 passes through the input channel and is rotatably connected. The herringbone gear shaft 142 assembly 14 is disposed within the input channel and is rotatably connected. The free end of the input gear shaft 13 is connected to the engine for transmission, and the free end of the herringbone gear shaft 142 assembly 14 is connected to the second-stage transmission mechanism for transmission. The engine drives the input gear shaft 13 to rotate, the input gear shaft 13 drives the herringbone gear shaft 142 assembly 14 to rotate, and the herringbone gear shaft 142 assembly 14 drives the second-stage transmission mechanism to rotate. By using the above-described first-stage transmission mechanism, the input gear shaft 13 and the herringbone gear shaft 142 assembly 14 are meshed together, which reduces the space occupied and makes the structure more compact.

[0046] In this embodiment, the input gear shaft 13 includes an input end and an output end. The input end extends to the outside of the input channel and is connected to the engine. The output end is rotatably connected to the input channel. A gear is provided between the input end and the output end, and the gear meshes with the gear portion of the herringbone gear shaft 142 assembly 14.

[0047] In this embodiment, the input channel is located below the first guide housing 8 and the second guide housing 37, that is, the input gear shaft 13 is located below the first guide housing 8 and the second guide housing 37. The purpose is that the input gear shaft 13 does not occupy the overall length of the fracturing pump, making the fracturing pump shorter in length and more compact in structure. Moreover, placing both the first-stage transmission mechanism and the second-stage transmission mechanism within the input channel facilitates the adjustment of the spatial position of the fracturing pump input shaft and is more conducive to the connection and setting with the output shaft of the engine and hydraulic transmission on the fracturing truck chassis.

[0048] Preferably, the herringbone gear shaft 142 assembly 14 includes an interference-fit herringbone gear shaft 142 and a first gear 141. The herringbone gear shaft 142 is connected to the second-stage transmission mechanism, and the first gear 141 is meshed with the input gear shaft 13. The herringbone gear shaft 142 and the input gear shaft 13 are parallel to each other. The first gear 141 is meshed with the gear on the input gear shaft 13, transmitting the engine torque to the first gear 141 of the herringbone gear shaft 142 assembly 14 via the input gear shaft 13. When the input gear shaft 13 drives the gear to rotate, it drives the first gear 141 to drive the herringbone gear shaft 142 to rotate, thereby realizing the transmission of force. Using the above-described herringbone gear shaft 142 assembly 14 results in a simple and compact structure that facilitates force transmission.

[0049] Preferably, first mounting holes are provided on opposite sides of the input channel, and a first cylindrical roller bearing 45 and a first tapered bearing 23 are respectively disposed in the two first mounting holes. The input gear shaft 13 is sequentially connected through the first cylindrical roller bearing 45 and the first tapered bearing 23. And / or second mounting holes are provided on opposite sides of the input channel, and a second cylindrical roller bearing 15 and a second tapered bearing 43 are respectively disposed in the two second mounting holes. The herringbone gear shaft 142 is sequentially connected through the second cylindrical roller bearing 15 and the second tapered bearing 43. The input gear shaft 13 is sequentially connected through the first cylindrical roller bearing 45 and the first tapered bearing 23 and is mounted on the input channel via the first cylindrical roller bearing 45 and the first tapered bearing 23; the herringbone gear shaft 142 is sequentially connected through the second cylindrical roller bearing 15 and the second tapered bearing 43 and is mounted on the input channel via the second cylindrical roller bearing 15 and the second tapered bearing 43. The first cylindrical roller bearing 45 gives the input gear shaft 13 a stronger load-bearing capacity, and the first tapered bearing 23 can limit the axial movement of the input gear shaft 13; similarly, the second cylindrical roller bearing 15 gives the herringbone gear shaft 142 a stronger load-bearing capacity, and the second tapered bearing 43 can limit the axial movement of the herringbone gear shaft 142.

[0050] Since the gear transmission in the first-stage transmission mechanism uses helical gears, which offer smooth transmission and high load-bearing capacity, the helical gear pair generates axial force. Considering the large loads on the left end of the input gear shaft 13 and the right end of the herringbone gear shaft 142 assembly 14, a cylindrical roller bearing structure with higher load-bearing capacity for the same size is adopted accordingly. Simultaneously, to limit the axial movement of the input gear shaft 13 and the herringbone gear shaft 142 assembly 14, face-to-face tapered bearing structures are used at the right end of the input gear shaft 13 and the left end of the herringbone gear shaft 142 assembly 14, respectively. That is, the bearing design of both the input gear shaft 13 and the first herringbone gear shaft assembly adopts a combination of one-end floating (NU-type cylindrical roller bearing) and one-end fixed (face-to-face tapered bearing). In this embodiment, the left end of the input gear shaft 13 is mounted on the housing via a first cylindrical roller bearing 45, and the right end of the input gear shaft 13 is mounted on the housing via a face-to-face tapered bearing 23 of the same type. The left end of the herringbone gear shaft 142 is mounted on the housing via a second tapered bearing 43 of the same type, which is installed face-to-face. The right end of the herringbone gear shaft 142 is mounted on the housing via a second cylindrical roller bearing 15.

[0051] Figure 8 for Figure 2 The diagram shows a herringbone gear assembly 21 at the power end of the fracturing pump. Figure 9 for Figure 2 The diagram shows a splined sleeve 22 on the power end of the fracturing pump. (See attached diagram.) Figure 8 and Figure 9 As shown, the second-stage transmission mechanism includes a herringbone gear assembly 21.

[0052] Preferably, the second-stage transmission mechanism includes a herringbone gear assembly 21, which is rotatably connected and housed within the gearbox. The input end of the herringbone gear assembly 21 meshes with the herringbone gear shaft 142, and the output end of the herringbone gear assembly 21 is provided with a spline sleeve 22. The first crankshaft 20 and the second crankshaft 35 are both splinedly connected to the spline sleeve 22. The herringbone gear shaft 142 drives the herringbone gear assembly 21 to rotate, which in turn drives the spline sleeve 22 to rotate. Simultaneously, the spline sleeve 22 drives the first crankshaft 20 and the second crankshaft 35 to rotate. Using this second-stage transmission mechanism, the herringbone gear assembly 21 and the herringbone gear shaft 142 mesh without additional axial force, resulting in a longer gear transmission life. It also reduces space requirements, making the structure more compact. The cooperation between the herringbone gear assembly 21 and the herringbone gear shaft 142 eliminates the need to consider the width of the hobbing groove in the center of the overall herringbone gear, allowing for gears with smaller tooth widths and minimizing the length of the fracturing pump.

[0053] Preferably, bearing housings are provided at the ends of the first crankshaft 20 housing 17 and the second crankshaft 35 housing 31 facing the gearbox, and cylindrical roller bearings 19 are provided on both bearing housings. The herringbone gear assembly 21 is respectively mounted on two cylindrical roller bearings on opposite sides. The herringbone gear assembly 21 is rotatably connected to the first crankshaft 20 housing 17 and the second crankshaft 35 housing 31 on both sides via the two cylindrical roller bearings, enabling effective torque transmission. Simultaneously, the herringbone gear assembly 21 is supported by two identical cylindrical roller bearings 19 with separable outer and inner rings, facilitating installation and providing strong load-bearing capacity.

[0054] In this embodiment, the cylindrical roller bearing is an NJ type cylindrical roller bearing. The NJ type bearings used in pairs can reserve a certain amount of free play in the axial direction. The purpose is to allow the herringbone gear assembly to "automatically center" under the action of the herringbone gear shaft 142 assembly 14 and find the optimal meshing position.

[0055] Preferably, the herringbone gear assembly 21 includes a herringbone gear hub and a left-handed herringbone gear and a right-handed herringbone gear respectively fitted on opposite sides of the herringbone gear hub. The herringbone gear hub has mounting holes, and a spline sleeve 22 is disposed within these mounting holes. The spline sleeve 22 secures the herringbone gear assembly 21 to the first crankshaft 20 and to the second crankshaft 35, thereby improving the connection strength.

[0056] In this embodiment, the left-hand herringbone gear 213 and the right-hand herringbone gear 215 are arranged opposite each other and spaced apart. The cylindrical pin 216 passes through the left-hand herringbone gear 213, the herringbone gear hub 214 and the right-hand herringbone gear 215 in sequence. By adding a first anti-loosening washer 212, the connection strength of the three can be improved. The screw 217 passes through the left-hand herringbone gear 213, the herringbone gear hub 214, the right-hand herringbone gear 215 and the first anti-loosening washer 216, and is limited by a nut 211.

[0057] The torque transmitted from the herringbone gear shaft 142 assembly 14 to the herringbone gear assembly 21 is transmitted to the first crankshaft 20 and the second crankshaft 35 via a spline connection. In this embodiment, a first external spline 221 is provided on the outer wall of the spline sleeve 22, a first internal spline 222 is provided on the inner wall of the spline sleeve 22, a second internal spline is provided on the inner wall of the mounting hole, and a second external spline is provided on the left end of the first crankshaft 20 and the right end of the second crankshaft 35. The first external spline 221 of the spline sleeve 22 is connected to the second internal spline of the mounting hole of the herringbone gear assembly 21, and the second external splines of the first crankshaft 20 and the second crankshaft 35 are both connected to the first internal spline 222 of the spline sleeve 22. To limit left and right movement, a retaining ring groove is provided on the inner wall of the spline sleeve 22.

[0058] The following section further describes the assembly and usage process of the fracturing pump's power end.

[0059] The assembly process is as follows:

[0060] The herringbone gear assembly 21 is formed by assembling the nut 211, the first anti-loosening washer 212, the herringbone left-hand gear 213, the herringbone gear hub 214, the herringbone right-hand gear 215, the cylindrical pin 216, and the screw 217. The herringbone gear assembly 21 is placed inside the gearbox. Bearing seats 18 are provided at the right end of the first crankshaft housing 1717 and the left end of the second crankshaft housing 31. Each bearing seat 18 is provided with a cylindrical roller bearing 19. 1. The crankshaft is connected to the first crankshaft housing 1717 and the second crankshaft housing 31 via cylindrical roller bearings 19 on both sides. The first crankshaft 20 and the second crankshaft 35 are respectively disposed in the first crankshaft housing 1717 and the second crankshaft housing 31. The first external spline 221 of the spline sleeve 22 is connected to the second internal spline of the mounting hole of the herringbone gear assembly 21. The second external splines of the first crankshaft 20 and the second crankshaft 35 are both connected to the first internal spline 222 of the spline sleeve 22. A retaining ring groove 223 is provided in the inner wall of the spline sleeve 22 to restrict left and right movement.

[0061] The first gear 141 and the herringbone gear shaft 142 are interference-fitted to form the herringbone gear shaft assembly 14. The first gear 141 meshes with the herringbone gear assembly 21. The left end of the herringbone gear shaft 142 is mounted on the input channel of the housing 46 via a second tapered bearing 43 of the same type, which is mounted face-to-face. The right end of the herringbone gear shaft 142 is mounted on the input channel via a second cylindrical roller bearing 15, which is fitted with a second shaft retaining ring 16. The end cover 26 is placed over the right end of the input channel using a first bolt 27 and a lock nut 25 to align the herringbone gear. The axle 142 is sealed and limited. The left end of the input gear shaft 13 is mounted on the input channel via a first cylindrical roller bearing 45 and a first shaft retaining ring 44. The right end of the input gear shaft 13 extends out of the input channel and connects to the engine. The input gear shaft 13 is mounted on the input channel via a first tapered bearing 23 of the same type, mounted face-to-face, and a first locking washer 24. A second bolt 29, a first lip seal 30, and an input gear shaft cover 28 are installed on the right end of the input channel to seal and limit the input gear shaft 13. The gear end cover 12 is fixed to the input channel by a second screw 11 to seal and limit the left ends of the input gear shaft 13 and the herringbone gear shaft 142. A fourth bolt 38, a shaft retaining ring 39, a bearing cap 40, a second anti-loosening washer 41, and a fifth bolt 42 are used to seal and limit the left end of the input channel.

[0062] The first guide housing 8 and the second guide housing 37 are respectively covered onto the first crankshaft housing 17 (including gearbox housing) 17 and the second crankshaft housing (including gearbox housing) 31; the first guide housing 8 and the second guide housing 37 are respectively connected to the first crankshaft housing 17 17 and the second crankshaft housing 37 by pins 9 and first screws 10. Multiple crossheads and connecting rod assemblies 36 are respectively provided on the first crankshaft 20 and the second crankshaft 35. The ends of the multiple crossheads and connecting rod assemblies 36 of the first crankshaft 20 away from the first crankshaft housing 1717 pass through the through holes of the first guide housing 8. The ends of the multiple crossheads and connecting rod assemblies 36 of the second crankshaft 35 away from the second crankshaft housing 31 pass through the through holes of the second guide housing 37. The oil seal mounting seat 5 is sleeved on the crosshead and connecting rod assembly 36 and connected to the first guide housing 8 and the second guide housing 37 by hexagonal screws 6. A cloth-reinforced oil-resistant gasket 7 is provided between the oil seal mounting seat 5 and the first guide housing 8 and the second guide housing 37. The axial oil seal 4 is connected to the oil seal mounting seat 5 and sleeved on the crosshead and connecting rod assembly 36. A retaining ring 3 is provided between the axial oil seal 4 and the oil seal mounting seat 5. The through holes of the first guide housing 8 and the second guide housing 37 are sealed by the oil seal mounting seat 5 and the axial oil seal 4. The first end of the connecting rod 2 passes through the first crankshaft housing 1717 and the first guide housing 8, the second crankshaft housing 31 and the second guide housing 37, which are arranged opposite to each other. The second end of the connecting rod 2 is provided with a hydraulic end clamping nut 1. A third bolt 33, a second lip seal 34 and a crankshaft bearing cover 32 are installed on the right end of the second crankshaft housing 31 and the left end of the first crankshaft housing 1717 to seal and limit the first crankshaft 20 and the second crankshaft 35.

[0063] The gear of the input gear shaft 13 meshes with the first gear 141 of the herringbone gear shaft assembly 14, the herringbone gear shaft 142 meshes with the herringbone gear assembly 21, and is fixed to the first crankshaft 20 and the second crankshaft 35 on both sides through the spline sleeve 22.

[0064] The usage process is as follows:

[0065] The engine drives the input gear shaft 13 to rotate, the gear of the input gear shaft 13 drives the first gear 141 to rotate, the first gear 141 drives the herringbone gear shaft 142 to rotate, the herringbone gear shaft 142 drives the herringbone gear assembly 21 to rotate, and the herringbone gear assembly 21 drives the first crankshaft 20 and the second crankshaft 35 to rotate synchronously through the spline sleeve 22.

[0066] The present invention also proposes a fracturing pump, which includes the fracturing pump power end as described above.

[0067] As can be seen from the above description and practice, the fracturing pump power end and the fracturing pump including the present invention have the following advantages compared with the prior art: the fracturing pump power end adopts a two-stage transmission method to achieve deceleration. Under the same or greater speed ratio, the diameter of the large gear of the power end reduction is reduced to reduce the maximum external size of the power end, thereby minimizing the length and height of the fracturing pump, maximizing the stroke of the fracturing pump and minimizing the number of strokes, thereby improving the service life of the fracturing pump's vulnerable parts.

[0068] Those skilled in the art should understand that the above description is merely a specific embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the scope of the present invention should be included within the protection scope of the present invention.

Claims

1. A fracturing pump power end characterized by, The box is communicated with an input channel, and first and second crankshafts are arranged in the box and distributed on opposite sides of the input channel. A transmission mechanism is arranged in the input channel, and the transmission mechanism comprises a first-stage transmission mechanism and a second-stage transmission mechanism which are in transmission connection, a free end of the first-stage transmission mechanism is in transmission connection with the engine, and a free end of the second-stage transmission mechanism is in transmission connection with the first and second crankshafts.

2. The power end of the fracturing pump according to claim 1, wherein: The box comprises a gear box and first and second crankshaft boxes which are respectively communicated on opposite sides of the gear box, first and second guide boxes are respectively connected to the first and second crankshaft boxes, the input channel is arranged on the gear box, the first and second crankshafts are respectively arranged in the first and second crankshaft boxes, at least two opposite connecting rod assemblies are arranged on the first and second crankshafts, the connecting rod assemblies on the first crankshaft can reciprocate through the first crankshaft box and the first guide box, and the connecting rod assemblies on the second crankshaft can reciprocate through the second crankshaft box and the second guide box.

3. The power end of the fracturing pump according to claim 2, wherein: The first and / or second crankshaft boxes are detachably connected to the gear box.

4. The power end of the fracturing pump according to any one of claims 1 to 3, wherein: The first-stage transmission mechanism comprises an input gear shaft and a herringbone gear shaft assembly which are in meshing connection, the input gear shaft is rotatably connected and penetrates the input channel, the herringbone gear shaft assembly is rotatably arranged in the input channel, a free end of the input gear shaft is in transmission connection with the engine, and a free end of the herringbone gear shaft assembly is in transmission connection with the second-stage transmission mechanism.

5. The power end of the fracturing pump according to claim 4, wherein: The herringbone gear shaft assembly comprises a herringbone gear shaft and a first gear which are in interference fit, the herringbone gear shaft is in transmission connection with the second-stage transmission mechanism, and the first gear is in meshing connection with the input gear shaft.

6. The power end of the fracturing pump according to claim 5, wherein: First mounting holes are respectively arranged on opposite sides of the input channel, a first cylindrical roller bearing and a first tapered bearing are respectively arranged in the first mounting holes, and the input gear shaft is sequentially connected and penetrates the first cylindrical roller bearing and the first tapered bearing; and / or second mounting holes are respectively arranged on opposite sides of the input channel, a second cylindrical roller bearing and a second tapered bearing are respectively arranged in the second mounting holes, and the herringbone gear shaft is sequentially connected and penetrates the second cylindrical roller bearing and the second tapered bearing.

7. The power end of the fracturing pump according to claim 6, wherein: ​ The second-stage transmission mechanism comprises a double-helical gear assembly, which is arranged in the gear box and rotatably connected, an input end of the double-helical gear assembly is in meshing connection with the double-helical gear shaft, and an output end of the double-helical gear assembly is provided with a spline sleeve, and the first crankshaft and the second crankshaft are connected with the spline sleeve through splines.

8. The fracturing pump power end of claim 7, characterized in that: The first crankshaft box and the second crankshaft box are both provided with bearing seats at one end towards the gear box, and both of the bearing seats are provided with cylindrical roller bearings, and opposite sides of the double-helical gear assembly are respectively arranged in the cylindrical roller bearings.

9. The fracturing pump power end of claim 8, characterized in that: The double-helical gear assembly comprises a double-helical gear hub, a left-handed double-helical gear and a right-handed double-helical gear which are respectively sleeved on opposite sides of the double-helical gear hub, the double-helical gear hub is provided with a mounting hole, and the spline sleeve is arranged in the mounting hole.

10. A fracturing pump characterized by: The fracturing pump comprises the fracturing pump power end according to any one of claims 1 to 9.

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