Powershift transmission and traction engineering machine

Abstract

A powershift transmission and a traction engineering machine. The powershift transmission comprises an input shaft (IN) and an output shaft (OUT), wherein a first planetary gearset (P1) and a second planetary gearset (P2) are sequentially provided in parallel on the input shaft; a third planetary gearset (P3), a fourth planetary gearset (P4), a fifth planetary gearset (P5) and a first clutch (C1) are sequentially provided in parallel on the output shaft; a reverse-gear brake (BR) is arranged on the first planetary gearset; a forward-gear brake (BF) is arranged on the second planetary gearset; a third-gear brake (B3) is arranged on the third planetary gearset; a fourth-gear brake (B4) is arranged on the fourth planetary gearset; and a second-gear brake (B2) is arranged on the fifth planetary gearset. The powershift transmission can realize four forward gears and four backward gears, the step ratios of the transmission ratios of the gears are in the range of 1.2 to 1.8, and the powershift transmission has the advantages of multiple gears, smooth gear shifting, and a compact structure.

Description

Power shift gearbox and traction type engineering machinery TECHNICAL FIELD

[0001] The present application belongs to the technical field of engineering machinery, and relates to a power shift gearbox and traction type engineering machinery. BACKGROUND

[0002] The traction type engineering machinery (for example, a bulldozer) has a poor working condition and a complex and changeable working condition, and how to improve the power performance and the economy is a problem that the bulldozer enterprise has been concerned about.

[0003] The traction performance is the most basic feature reflecting the power performance and the economy of the traction type engineering machinery, the traction power under different gears has a parabolic relationship with the vehicle speed, and the maximum traction power under each gear corresponds to a vehicle speed.

[0004] The power shift gearbox currently applied to the traction type engineering machinery mainly adopts a forward three-gear and reverse three-gear gearbox, and the maximum traction power can be exerted only at three vehicle speeds during operation. There are problems of few gears and large steps between the gear transmission ratios, and the maximum traction power cannot be fully utilized.

[0005] In order to maximize the power performance and the economy of the traction type engineering machinery, the gear distribution in the commonly used vehicle speed range should be improved as much as possible, and a planetary power shift gearbox with more gears and small and uniform steps is urgently needed to maximize the production efficiency of the traction type engineering machinery.

[0006] SUMMARY

[0007] The present application provides a power shift gearbox and traction type engineering machinery in view of at least one of the above technical problems.

[0008] Technical scheme: In order to solve the above technical problems, the technical scheme adopted by the present application is:

[0009] In a first aspect, a power shift gearbox is provided, comprising an input shaft and an output shaft, the input shaft is provided with a first planetary gear set and a second planetary gear set in sequence and side by side, the output shaft is provided with a third planetary gear set, a fourth planetary gear set, a fifth planetary gear set and a first clutch in sequence and side by side, a reverse brake is arranged on the first planetary gear set, a forward brake is arranged on the second planetary gear set, a third gear brake is arranged on the third planetary gear set, a fourth gear brake is arranged on the fourth planetary gear set, and a second gear brake is arranged on the fifth planetary gear set.

[0010] The first planetary gear train includes a first sun gear, a first planet carrier, a first planet gear and a first ring gear, the first planet gear is movably installed on the first planet carrier, the first ring gear is engaged with the first planet gear, the first planet gear is engaged with the first sun gear, the first planet carrier is braked by the reverse brake;

[0011] The second planetary gear train includes a second sun gear, a second planet carrier, a second planet gear and a second ring gear, the second planet gear is movably installed on the second planet carrier, the second ring gear is engaged with the second planet gear, the second planet gear is engaged with the second sun gear, the second ring gear is braked by the forward brake;

[0012] The third planetary gear train includes a third sun gear, a third planet carrier, a third planet gear and a third ring gear, the third planet gear is movably installed on the third planet carrier, the third ring gear is engaged with the third planet gear, the third planet gear is engaged with the third sun gear, the third ring gear is braked by the third brake;

[0013] The fourth planetary gear train includes a fourth sun gear, a fourth planet carrier, a fourth planet gear and a fourth ring gear, the fourth planet gear is movably installed on the fourth planet carrier, the fourth ring gear is engaged with the fourth planet gear, the fourth planet gear is engaged with the fourth sun gear, the fourth ring gear is braked by the fourth brake;

[0014] The fifth planetary gear train includes a fifth sun gear, a fifth planet carrier, a fifth planet gear and a fifth ring gear, the fifth planet gear is movably installed on the fifth planet carrier, the fifth ring gear is engaged with the fifth planet gear, the fifth planet gear is engaged with the fifth sun gear, the fifth ring gear is braked by the second brake;

[0015] The inner hub of the first clutch is fixedly connected with the output shaft, and the outer hub of the first clutch is fixedly connected with the fifth ring gear;

[0016] The first sun gear and the second sun gear are connected with the input shaft, the third sun gear, the fourth sun gear and the fifth sun gear are fixedly connected with the output shaft, the first ring gear is fixedly connected with the second planet carrier, the second planet carrier is fixedly connected with the third planet carrier, the third ring gear is fixedly connected with the fourth planet carrier, and the fourth ring gear is fixedly connected with the fifth planet carrier.

[0017] In some embodiments, the forward gear brake and the reverse gear brake are direction control clutches, and the first clutch, the second gear brake, the third gear brake and the fourth gear brake are gear control clutches; the forward gear is achieved by engaging the forward gear brake, the reverse gear is achieved by engaging the reverse gear brake, the first gear is achieved by engaging the first clutch, the second gear is achieved by engaging the second gear brake, the third gear is achieved by engaging the third gear brake, and the fourth gear is achieved by engaging the fourth gear brake.

[0018] In some embodiments, the forward gear brake is engaged simultaneously with the first clutch to achieve forward first gear; the forward gear brake is engaged simultaneously with the second gear brake to achieve forward second gear; the forward gear brake is engaged simultaneously with the third gear brake to achieve forward third gear; the forward gear brake is engaged simultaneously with the fourth gear brake to achieve forward fourth gear; the reverse gear brake is engaged simultaneously with the first clutch to achieve reverse first gear; the reverse gear brake is engaged simultaneously with the second gear brake to achieve reverse second gear; the reverse gear brake is engaged simultaneously with the third gear brake to achieve reverse third gear; and the reverse gear brake is engaged simultaneously with the fourth gear brake to achieve reverse fourth gear; the step ratio of each gear transmission ratio is between 1.2 and 1.8.

[0019] In some embodiments, the forward gear brake is engaged simultaneously with the first clutch to fix the second ring gear, and simultaneously connect the fifth ring gear and the output shaft as a whole, and the second sun gear is connected with the input shaft through the spline to rotate in the same direction and at the same speed; in the second planetary gear set, the second sun gear inputs power, and the second carrier and the third carrier rotate in the same direction with the input shaft because the second ring gear is fixed by the forward gear brake; in the third planetary gear set, the third carrier inputs power, and the third sun gear and the third ring gear output power, the third sun gear is connected with the output shaft to drive the output shaft to rotate, and the third ring gear drives the fourth carrier to rotate; in the fourth planetary gear set, the fourth carrier inputs power, and the fourth sun gear and the fourth ring gear output power, the fourth sun gear is connected with the output shaft to drive the output shaft to rotate, and the fourth ring gear drives the fifth carrier to rotate; in the fifth planetary gear set, the fifth carrier inputs power, and the fifth sun gear and the fifth ring gear output power as a whole because the first clutch is engaged to connect the fifth ring gear and the output shaft as a whole; finally, the power is output to the output shaft through the third sun gear, the fourth sun gear, the fifth sun gear and the fifth ring gear to achieve forward first gear.

[0020] In some embodiments, the forward gear brake and the second gear brake are engaged at the same time, respectively fixing the second ring gear and the fifth ring gear, the second sun gear rotates with the input shaft in the same direction and at the same speed through the spline connection; in the second planetary gear set, the second sun gear inputs power, the second carrier and the third carrier rotate with the input shaft in the same direction because the second ring gear is fixed by the forward gear brake; in the third planetary gear set, the third carrier inputs power, the third sun gear and the third ring gear output power, the third sun gear is connected with the output shaft to drive the output shaft to rotate, and the third ring gear drives the fourth carrier to rotate; in the fourth planetary gear set, the fourth carrier inputs power, the fourth sun gear and the fourth ring gear output power, the fourth sun gear is connected with the output shaft to drive the output shaft to rotate, and the fourth ring gear drives the carrier to rotate; in the fifth planetary gear set, the second gear brake is engaged to fix the fifth ring gear, and the fifth sun gear outputs power; finally, the third sun gear, the fourth sun gear and the fifth sun gear jointly output power to the output shaft to realize the second forward gear.

[0021] In some embodiments, the forward gear brake and the third gear brake are engaged at the same time, respectively fixing the second ring gear and the third ring gear, the second sun gear rotates with the input shaft in the same direction and at the same speed through the spline connection; in the second planetary gear set, the second sun gear inputs power, the second carrier and the third carrier rotate with the input shaft in the same direction because the second ring gear is fixed by the forward gear brake; in the third planetary gear set, the third carrier inputs power, the third ring gear is fixed by the engagement of the third gear brake, and the third sun gear outputs power; finally, the third sun gear outputs power to the output shaft to realize the third forward gear.

[0022] In some embodiments, the forward gear brake and the fourth gear brake are engaged at the same time, respectively fixing the second ring gear and the fourth ring gear, the second sun gear rotates with the input shaft in the same direction and at the same speed through the spline connection; in the second planetary gear set, the second sun gear inputs power, the second carrier and the third carrier rotate with the input shaft in the same direction because the second ring gear is fixed by the forward gear brake; in the third planetary gear set, the third carrier inputs power, the third sun gear and the third ring gear output power, the third sun gear is connected with the output shaft to drive the output shaft to rotate, and the third ring gear drives the fourth carrier to rotate; in the fourth planetary gear set, the fourth carrier inputs power, the fourth ring gear is fixed by the engagement of the fourth gear brake, and the fourth sun gear outputs power; finally, the third sun gear and the fourth sun gear jointly output power to the output shaft to realize the fourth forward gear.

[0023] In some embodiments, the reverse brake is engaged simultaneously with the first clutch, respectively fixing the first carrier, and connecting the fifth ring gear and the output shaft as a whole, and the first sun gear is connected with the input shaft through the spline to rotate in the same direction and at the same speed; in the first planetary gear set, the first sun gear inputs power, and the first ring gear rotates reversely with the first sun gear and outputs power, while driving the third carrier to rotate; in the third planetary gear set, the third carrier inputs power, and the third sun gear and the third ring gear output power, the third sun gear is connected with the output shaft to drive the output shaft to rotate, and the third ring gear drives the fourth carrier to rotate; in the fourth planetary gear set, the fourth carrier inputs power, and the fourth sun gear and the fourth ring gear output power, the fourth sun gear is connected with the output shaft to drive the output shaft to rotate, and the fourth ring gear drives the fifth carrier to rotate; in the fifth planetary gear set, the fifth carrier inputs power, and the fifth sun gear and the fifth ring gear output power as a whole because the first clutch is engaged to connect the fifth ring gear and the output shaft as a whole; finally, the power is output to the output shaft through the third sun gear, the fourth sun gear, the fifth sun gear and the fifth ring gear, realizing the reverse first gear.

[0024] In some embodiments, the reverse brake is engaged simultaneously with the second gear brake, respectively fixing the first carrier and the fifth ring gear, and the first sun gear is connected with the input shaft through the spline to rotate in the same direction and at the same speed; in the first planetary gear set, the first sun gear inputs power, and the first ring gear rotates reversely with the first sun gear and outputs power, while driving the third carrier to rotate; in the third planetary gear set, the third carrier inputs power, and the third sun gear and the third ring gear output power, the third sun gear is connected with the output shaft to drive the output shaft to rotate, and the third ring gear drives the fourth carrier to rotate; in the fourth planetary gear set, the fourth carrier inputs power, and the fourth sun gear and the fourth ring gear output power, the fourth sun gear is connected with the output shaft to drive the output shaft to rotate, and the fourth ring gear drives the fifth carrier to rotate; in the fifth planetary gear set, the second gear brake is engaged to fix the fifth ring gear, and the fifth sun gear outputs power; finally, the third sun gear, the fourth sun gear and the fifth sun gear output power to the output shaft, realizing the reverse second gear.

[0025] In some embodiments, the reverse brake is engaged simultaneously with the third brake, fixing the first carrier and the third ring gear respectively, the first sun gear rotates with the input shaft in the same direction and at the same speed; in the first planetary gear set, the first sun gear inputs power, the first ring gear rotates reversely with the first sun gear and outputs power, driving the third carrier to rotate at the same time; in the third planetary gear set, the third carrier inputs power, the third sun gear outputs power with the third ring gear, the third sun gear is connected with the output shaft, driving the output shaft to rotate, the third ring gear drives the fourth carrier to rotate; in the fourth planetary gear set, the fourth carrier inputs power, the fourth ring gear is fixed by the engagement of the fourth brake, the fourth sun gear outputs power; finally, the third sun gear and the fourth sun gear output power to the output shaft together, realizing reverse four gears.

[0026] In some embodiments, the reverse brake is engaged simultaneously with the fourth brake, fixing the first carrier and the fourth ring gear respectively, the first sun gear rotates with the input shaft in the same direction and at the same speed; in the first planetary gear set, the first sun gear inputs power, the first ring gear rotates reversely with the first sun gear and outputs power, driving the third carrier to rotate at the same time; in the third planetary gear set, the third carrier inputs power, the third sun gear outputs power with the third ring gear, the third sun gear is connected with the output shaft, driving the output shaft to rotate, the third ring gear drives the fourth carrier to rotate; in the fourth planetary gear set, the fourth carrier inputs power, the fourth ring gear is fixed by the engagement of the fourth brake, the fourth sun gear outputs power; finally, the third sun gear and the fourth sun gear output power to the output shaft together, realizing reverse four gears.

[0027] In some embodiments, the input shaft, the first sun gear, the second sun gear, the third sun gear, the fourth sun gear, the fifth sun gear and the output shaft are coaxially arranged.

[0028] In some embodiments, the ratio of the number of teeth of the first ring gear to the number of teeth of the first sun gear is 2.529;

[0029] The ratio of the number of teeth of the second ring gear to the number of teeth of the second sun gear is 2.143;

[0030] The ratio of the number of teeth of the third ring gear to the number of teeth of the third sun gear is 2.143;

[0031] The ratio of the number of teeth of the fourth ring gear to the number of teeth of the fourth sun gear is 1.824;

[0032] The ratio of the number of teeth of the fifth ring gear to the number of teeth of the fifth sun gear is 1.824.

[0033] In some embodiments, the transmission ratio range of the first forward gear is 3.14, the transmission ratio range of the second forward gear is 2.25, the transmission ratio range of the third forward gear is 1.76, and the transmission ratio range of the fourth forward gear is 1.00; the transmission ratio range of the first reverse gear is 2.53, the transmission ratio range of the second reverse gear is 1.81, the transmission ratio range of the third reverse gear is 1.42, and the transmission ratio range of the fourth reverse gear is 0.80.

[0034] In some embodiments, the step ratio of the first forward gear to the second forward gear is 1.40, the step ratio of the second forward gear to the third forward gear is 1.28, and the step ratio of the third forward gear to the fourth forward gear is 1.76; the step ratio of the first reverse gear to the second reverse gear is 1.40, the step ratio of the second reverse gear to the third reverse gear is 1.28, and the step ratio of the third reverse gear to the fourth reverse gear is 1.76.

[0035] In some embodiments, the reverse gear brake, the forward gear brake, the third gear brake, the fourth gear brake, the second gear brake, and the first clutch are all multi-plate friction control structures.

[0036] In the second aspect, a traction type engineering machine is provided, comprising the power shift transmission.

[0037] In some embodiments, the traction type engineering machine can be a bulldozer.

[0038] Advantages: The power shift transmission and the traction type engineering machine provided by the present application have the following advantages: the power shift transmission for the traction type engineering machine of the present application comprises five planetary rows, five brakes, and a clutch, the planetary rows are all single-planet simple planetary rows, there are four forward gears and four reverse gears, the transmission ratio distribution is uniform and the step ratio is small, the maximum traction power can be fully exerted in the working condition, and the production efficiency of the whole machine is improved. The five brakes and the clutch are all multi-plate friction control structures, the piston is pushed by hydraulic oil to brake, four forward gears and four reverse gears are realized, the step ratio of the transmission ratio of each gear during forward or reverse movement is in the range of 1.2-1.8, the power shift transmission has the advantages of many gears, good gear shifting smoothness, and compact structure, and is suitable for track type traction type engineering machines. BRIEF DESCRIPTION OF DRAWINGS

[0039] Fig. 1 is a schematic view of a power shift transmission according to an embodiment of the present application;

[0040] Fig. IN - input shaft; OUT - output shaft; PI - first planetary row; P2 - second planetary row; P3 - third planetary row; P4 - fourth planetary row; P5 - fifth planetary row; BR - reverse brake; BF - forward brake; B4 - fourth gear brake; B3 - third gear brake; B2 - second gear brake; CI - first clutch; SI - first sun gear; S2 - second sun gear; S3 - third sun gear; S4 - fourth sun gear; S5 - fifth sun gear; PCI - first carrier; PC2 - second carrier; PC3 - third carrier; PC4 - fourth carrier; PC5 - fifth carrier; Rl - first ring gear; R2 - second ring gear; R3 - third ring gear; R4 - fourth ring gear; R5 - fifth ring gear. DETAILED DESCRIPTION

[0041] The technical solutions in the embodiments of the present application will be described clearly and completely below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. The description of the at least one exemplary embodiment is actually only illustrative, but not as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without any creative effort belong to the scope of protection of the present application.

[0042] Unless specifically stated otherwise, the relative arrangements of the components and steps, numerical expressions, and numerical values set forth in the various examples herein are not limiting of the scope of the application. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and not of limitation. The detailed description of the exemplary embodiments should be considered in connection with the accompanying drawings, and not in a isolation. Any techniques, methods, and apparatus known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered part of the specification, if appropriate. In all examples shown and discussed herein, any specific values should be interpreted as merely illustrative and not as a limitation on the scope of the exemplary embodiments. Thus, other examples of the exemplary embodiments can have different values. It is noted that like references and letters designate like items in the following drawings and description thereof, and thus, no further discussion relating to such items is deemed necessary.

[0043] In the description of the application, it needs to be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the application and simplifying the description, and does not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the application. In addition, the terms "first", "second" and the like are only for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined with "first", "second" and the like can be explicitly or implicitly included one or more. In the description of the application, unless otherwise stated, the meaning of "a plurality of" is two or more.

[0044] In the description of the application, it needs to be understood that unless otherwise explicitly specified and limited, the terms "mounting", "connecting", "connection" should be understood broadly, for example, it can be fixed connection, or detachable connection, or integrally connected; it can be mechanical connection, or electrical connection; it can be directly connected, or indirectly connected through intermediate medium, or the communication inside two elements. For those skilled in the art, the specific meaning of the above terms in the application can be understood through specific circumstances.

[0045] Embodiment 1: A power shift gearbox, comprising an input shaft IN and an output shaft OUT, the input shaft IN is provided with a first planetary gear set P1 and a second planetary gear set P2 in sequence and side by side; the output shaft OUT is provided with a third planetary gear set P3, a fourth planetary gear set P4, a fifth planetary gear set P5 and a first clutch C1 in sequence and side by side; the first planetary gear set P1 is provided with a reverse brake BR, the second planetary gear set P2 is provided with a forward brake BF, the third planetary gear set P3 is provided with a third gear brake B3, the fourth planetary gear set P4 is provided with a fourth gear brake B4, and the fifth planetary gear set P5 is provided with a second gear brake B2;

[0046] The forward brake BF and the reverse brake BR are direction control clutches, and the first clutch C1, the second gear brake B2, the third gear brake B3 and the fourth gear brake B4 are gear control clutches;

[0047] The forward gear brake BF is engaged with the first clutch C1 at the same time to realize the first forward gear; the forward gear brake BF is engaged with the second gear brake B2 at the same time to realize the second forward gear; the forward gear brake BF is engaged with the third gear brake B3 at the same time to realize the third forward gear; the forward gear brake BF is engaged with the fourth gear brake B4 at the same time to realize the fourth forward gear; the reverse gear brake BR is engaged with the first clutch C1 at the same time to realize the first reverse gear; the reverse gear brake BR is engaged with the second gear brake B2 at the same time to realize the second reverse gear; the reverse gear brake BR is engaged with the third gear brake B3 at the same time to realize the third reverse gear; the reverse gear brake BR is engaged with the fourth gear brake B4 at the same time to realize the fourth reverse gear; the step ratio of each gear transmission ratio is 1.2-1.8.

[0048] In some embodiments, the reverse gear brake BR is used to brake the first planet carrier PC1 of the first planetary row P1, the forward gear brake BF is used to brake the second ring gear R2 of the second planetary row P2, the third gear brake B3 is used to brake the third ring gear R3 of the third planetary row P3, the fourth gear brake B4 is used to brake the fourth ring gear R4 of the fourth planetary row P4, and the second gear brake B2 is used to brake the fifth ring gear R5 of the fifth planetary row P5.

[0049] In some embodiments, a traction type power shift gearbox for engineering machinery is shown in FIG. 1, which includes a first planetary row P1, a second planetary row P2, a third planetary row P3, a fourth planetary row P4, a fifth planetary row P5 and a first clutch C1 arranged in sequence and side by side;

[0050] The first planetary row P1 includes a first sun gear S1, a first planet carrier PC1, a first planet gear CA1 and a first ring gear R1, the first planet gear CA1 is movably mounted on the first planet carrier PC1, the first ring gear R1 is engaged with the first planet gear CA1, the first planet gear CA1 is engaged with the first sun gear S1, and the first planet carrier PC1 is braked by the reverse gear brake BR;

[0051] The second planetary row P2 includes a second sun gear S2, a second planet carrier PC2, a second planet gear CA2 and a second ring gear R2, the second planet gear CA2 is movably mounted on the second planet carrier PC2, the second ring gear R2 is engaged with the second planet gear CA2, the second planet gear CA2 is engaged with the second sun gear S2, and the second ring gear R2 is braked by the forward gear brake BF;

[0052] The third planetary gear set P3 comprises a third sun gear S3, a third planet carrier PC3, third planet gears CA3 movably mounted on the third planet carrier PC3, and a third ring gear R3 engaged with the third planet gears CA3, the third planet gears CA3 being engaged with the third sun gear S3, the third ring gear R3 being braked by the third gear brake B3;

[0053] The fourth planetary gear set P4 comprises a fourth sun gear S4, a fourth planet carrier PC4, fourth planet gears CA4 movably mounted on the fourth planet carrier PC4, and a fourth ring gear R4 engaged with the fourth planet gears CA4, the fourth planet gears CA4 being engaged with the fourth sun gear S4, the fourth ring gear R4 being braked by the fourth gear brake B4;

[0054] The fifth planetary gear set P5 comprises a fifth sun gear S5, a fifth planet carrier PC5, fifth planet gears CA5 movably mounted on the fifth planet carrier PC5, and a fifth ring gear R5 engaged with the fifth planet gears CA5, the fifth planet gears CA5 being engaged with the fifth sun gear S5, the fifth ring gear R5 being braked by the second gear brake B2.

[0055] The inner hub of the first clutch C1 is fixedly connected with the output shaft, and the outer hub of the first clutch C1 is fixedly connected with the fifth ring gear R5.

[0056] The first sun gear S1 and the second sun gear S2 are connected with the input shaft; the third sun gear S3, the fourth sun gear S4, and the fifth sun gear S5 are fixedly connected with the output shaft; the first ring gear R1 is fixedly connected with the second planet carrier PC2; the second planet carrier PC2 is fixedly connected with the third planet carrier PC3, the third ring gear R3 is fixedly connected with the fourth planet carrier PC4, and the fourth ring gear R4 is fixedly connected with the fifth planet carrier PC5.

[0057] In some embodiments, the input shaft IN, the first sun gear S1, the second sun gear S2, the third sun gear S3, the fourth sun gear S4, the fifth sun gear S5, and the output shaft OUT are coaxially arranged.

[0058] In some embodiments, the reverse gear brake BR, the forward gear brake BF, the third gear brake B3, the fourth gear brake B4, the second gear brake B2, and the first clutch C1 are all multi-plate friction actuation structures; a piston is pushed by hydraulic oil to brake.

[0059] Further, in some embodiments, the control logic and the gear ratios of each gear are as shown in Table 1.

[0060] Table 1. Gear control logic and gear ratio (O indicates the engagement of the operating member)

[0061] The example of the present application is described in detail below in conjunction with Fig. 1 and Table 1, where the gear ratio refers to the ratio of the input shaft speed to the output shaft speed.

[0062] The forward brake BF is engaged at the same time as the first clutch CI, fixing the second ring gear R2 and connecting the fifth ring gear R5 and the output shaft as a whole, and the second sun gear S2 is connected to the input shaft IN through the spline, rotating in the same direction and at the same speed; in the second planetary gear set, the second sun gear S2 inputs power, and the second carrier PC2 and the third carrier PC3 rotate in the same direction as the input shaft because the second ring gear R2 is fixed by the forward brake BF; in the third planetary gear set, the third carrier PC3 inputs power, and the third sun gear S3 and the third ring gear R3 output power, the third sun gear S3 is connected to the output shaft OUT, driving the output shaft to rotate, and the third ring gear R3 drives the fourth carrier PC4 to rotate; in the fourth planetary gear set, the fourth carrier PC4 inputs power, and the fourth sun gear S4 and the fourth ring gear R4 output power, the fourth sun gear S4 is connected to the output shaft OUT, driving the output shaft to rotate, and the fourth ring gear R4 drives the fifth carrier PC5 to rotate; in the fifth planetary gear set, the fifth carrier PC5 inputs power, and the fifth ring gear R5 and the output shaft OUT are connected as a whole because the first clutch CI is engaged, and the fifth sun gear S5 and the fifth ring gear R5 jointly output power; finally, the power is jointly output from the third sun gear S3, the fourth sun gear S4, the fifth sun gear S5, and the fifth ring gear R5 to the output shaft, realizing the forward first gear;

[0063] The forward gear brake BF is engaged at the same time as the second gear brake B2, and the second ring gear R2 and the fifth ring gear R5 are fixed respectively, the second sun gear S2 rotates with the input shaft IN through the spline connection in the same direction and at the same speed; in the second planetary gear set, the second sun gear S2 inputs power, and the second carrier PC2 and the third carrier PC3 rotate with the input shaft in the same direction because the second ring gear R2 is fixed by the forward gear brake BF; in the third planetary gear set, the third carrier PC3 inputs power, and the third sun gear S3 and the third ring gear R3 output power, the third sun gear S3 is connected with the output shaft OUT to drive the output shaft to rotate, and the third ring gear R3 drives the fourth carrier PC4 to rotate; in the fourth planetary gear set, the fourth carrier PC4 inputs power, and the fourth sun gear S4 and the fourth ring gear R4 output power, the fourth sun gear S4 is connected with the output shaft OUT to drive the output shaft to rotate, and the fourth ring gear R4 drives the fifth carrier PC5 to rotate; in the fifth planetary gear set, the second gear brake B2 is engaged to fix the fifth ring gear R5, and the fifth sun gear S5 outputs power; finally, the third sun gear S3, the fourth sun gear S4 and the fifth sun gear S5 jointly output power to the output shaft to realize the forward second gear;

[0064] The forward gear brake BF is engaged at the same time as the third gear brake B3, and the second ring gear R2 and the third ring gear R3 are fixed respectively, the second sun gear S2 rotates with the input shaft IN through the spline connection in the same direction and at the same speed; in the second planetary gear set, the second sun gear S2 inputs power, and the second carrier PC2 and the third carrier PC3 rotate with the input shaft in the same direction because the second ring gear R2 is fixed by the forward gear brake BF; in the third planetary gear set, the third carrier PC3 inputs power, and the third sun gear S3 outputs power because the third gear brake B3 is engaged to fix the third ring gear R3; finally, the third sun gear S3 outputs power to the output shaft to realize the forward third gear;

[0065] The forward gear brake BF is engaged simultaneously with the fourth gear brake B4, and the second ring gear R2 and the fourth ring gear R4 are fixed respectively, the second sun gear S2 and the input shaft IN are connected through the spline and rotate in the same direction and at the same speed; in the second planetary gear set, the second sun gear S2 inputs power, and the second carrier PC2 and the third carrier PC3 rotate in the same direction with the input shaft because the second ring gear R2 is fixed by the forward gear brake BF; in the third planetary gear set, the third carrier PC3 inputs power, the third sun gear S3 and the third ring gear R3 output power, the third sun gear S3 is connected with the output shaft OUT and drives the output shaft to rotate, and the third ring gear R3 drives the fourth carrier PC4 to rotate; in the fourth planetary gear set, the fourth carrier PC4 inputs power, and the fourth sun gear S4 outputs power because the fourth gear brake B4 is engaged to fix the fourth ring gear R4; finally, the third sun gear S3 and the fourth sun gear S4 jointly output power to the output shaft, realizing the forward fourth gear.

[0066] The reverse gear brake BR is engaged simultaneously with the first clutch C1, and the first carrier PC1 is fixed, and the fifth ring gear R5 and the output shaft OUT are connected as a whole, and the first sun gear S1 and the input shaft IN are connected through the spline and rotate in the same direction and at the same speed; in the first planetary gear set, the first sun gear S1 inputs power, and the first ring gear R1 and the first sun gear S1 rotate in opposite directions and output power, and drive the third carrier PC3 to rotate at the same time because the first carrier PC1 is fixed by the reverse gear brake BR; in the third planetary gear set, the third carrier PC3 inputs power, the third sun gear S3 and the third ring gear R3 output power, the third sun gear S3 is connected with the output shaft OUT and drives the output shaft to rotate, and the third ring gear R3 drives the fourth carrier PC4 to rotate; in the fourth planetary gear set, the fourth carrier PC4 inputs power, the fourth sun gear S4 and the fourth ring gear R4 output power, the fourth sun gear S4 is connected with the output shaft OUT and drives the output shaft to rotate, and the fourth ring gear R4 drives the fifth carrier PC5 to rotate; in the fifth planetary gear set, the fifth carrier PC5 inputs power, and the fifth sun gear S5 and the fifth ring gear R5 jointly output power because the first clutch C1 is engaged to connect the fifth ring gear R5 and the output shaft OUT as a whole; finally, power is jointly output to the output shaft through the third sun gear S3, the fourth sun gear S4, the fifth sun gear S5 and the fifth ring gear R5, realizing the reverse first gear.

[0067] The reverse brake BR is engaged at the same time as the second gear brake B2, and the first planet carrier PC1 and the fifth ring gear R5 are fixed respectively, the first sun gear S1 rotates with the input shaft IN through the spline connection in the same direction and at the same speed; in the first planetary gear set, the first sun gear S1 inputs power, and since the first planet carrier PC1 is fixed by the reverse brake BR, the first ring gear R1 rotates in the opposite direction of the first sun gear S1 and outputs power, and drives the third planet carrier PC3 to rotate at the same time; in the third planetary gear set, the third planet carrier PC3 inputs power, the third sun gear S3 and the third ring gear R3 output power, the third sun gear S3 is connected with the output shaft OUT to drive the output shaft to rotate, and the third ring gear R3 drives the fourth planet carrier PC4 to rotate; in the fourth planetary gear set, the fourth planet carrier PC4 inputs power, the fourth sun gear S4 and the fourth ring gear R4 output power, the fourth sun gear S4 is connected with the output shaft OUT to drive the output shaft to rotate, and the fourth ring gear R4 drives the fifth planet carrier PC5 to rotate; in the fifth planetary gear set, the second gear brake B2 is engaged to fix the fifth ring gear R5, and the fifth sun gear S5 outputs power; finally, the third sun gear S3, the fourth sun gear S4 and the fifth sun gear S5 jointly output power to the output shaft to realize reverse two gears;

[0068] The reverse brake BR is engaged at the same time as the third gear brake B3, and the first planet carrier PC1 and the third ring gear R3 are fixed respectively, and the first sun gear S1 rotates with the input shaft IN through the spline connection in the same direction and at the same speed; in the first planetary gear set, the first sun gear S1 inputs power, and since the first planet carrier PC1 is fixed by the reverse brake BR, the first ring gear R1 rotates in the opposite direction of the first sun gear S1 and outputs power, and drives the third planet carrier PC3 to rotate; in the third planetary gear set, the third planet carrier PC3 inputs power, and since the third gear brake B3 is engaged, the third ring gear R3 is fixed, and the third sun gear S3 outputs power; finally, the third sun gear S3 outputs power to the output shaft to realize reverse three gears;

[0069] The reverse brake BR is engaged at the same time as the fourth brake B4, and the first planet carrier PC1 and the fourth ring gear R4 are fixed respectively, the first sun gear S1 rotates with the input shaft IN through the spline connection in the same direction and at the same speed; in the first planetary gear set, the first sun gear S1 inputs power, and since the first planet carrier PC1 is fixed by the reverse brake BR, the first ring gear R1 rotates in the opposite direction of the first sun gear S1 and outputs power, and at the same time drives the third planet carrier PC3 to rotate; in the third planetary gear set, the third planet carrier PC3 inputs power, the third sun gear S3 and the third ring gear R3 output power, the third sun gear S3 is connected with the output shaft OUT to drive the output shaft to rotate, and the third ring gear R3 drives the fourth planet carrier PC4 to rotate; in the fourth planetary gear set, the fourth planet carrier PC4 inputs power, and since the fourth brake B4 is engaged, the fourth ring gear R4 is fixed, and the fourth sun gear S4 outputs power; finally, the third sun gear S3 and the fourth sun gear S4 jointly output power to the output shaft, realizing the fourth reverse gear.

[0070] The transmission ratio of each gear described above is determined by the K value of the five planetary gear sets. The K value of the planetary gear set refers to the ratio of the number of teeth of the ring gear to the number of teeth of the sun gear. For example, when K1=2.529, K2=K3=2.143, and K4=K5=1.824, the transmission ratio of each gear shown in Table 1 is obtained, realizing the four forward gears and four reverse gears of the transmission mechanism, and meeting the requirements of the whole machine for multiple gears, smooth gear shifting, and compact structure of the transmission.

[0071] In some embodiments, the ratio of the number of teeth of the first ring gear R1 to the number of teeth of the first sun gear S1 is 2.529.

[0072] In some embodiments, the ratio of the number of teeth of the second ring gear R2 to the number of teeth of the second sun gear S2 is 2.143.

[0073] In some embodiments, the ratio of the number of teeth of the third ring gear R3 to the number of teeth of the third sun gear S3 is 2.143.

[0074] In some embodiments, the ratio of the number of teeth of the fourth ring gear R4 to the number of teeth of the fourth sun gear S4 is 1.824.

[0075] In some embodiments, the ratio of the number of teeth of the fifth ring gear R5 to the number of teeth of the fifth sun gear S5 is 1.824.

[0076] Further, in this embodiment, the transmission ratio range of the first forward gear is 3.14, the transmission ratio range of the second forward gear is 2.25, the transmission ratio range of the third forward gear is 1.76, and the transmission ratio range of the fourth forward gear is 1.00; the transmission ratio range of the first reverse gear is 2.53, the transmission ratio range of the second reverse gear is 1.81, the transmission ratio range of the third reverse gear is 1.42, and the transmission ratio range of the fourth reverse gear is 0.80.

[0077] Further, in the embodiment, the step ratio of the first forward gear to the second forward gear is 1.40, the step ratio of the second forward gear to the third forward gear is 1.28, and the step ratio of the third forward gear to the fourth forward gear is 1.76; the step ratio of the first reverse gear to the second reverse gear is 1.40, the step ratio of the second reverse gear to the third reverse gear is 1.28, and the step ratio of the third reverse gear to the fourth reverse gear is 1.76.

[0078] The embodiment discloses a power shift gearbox for a traction type engineering machine, as shown in FIG. 1, which comprises an input shaft IN, an output shaft OUT, five planetary gears (P1-P5), five brakes (BR, BF, B2-B4) and a clutch (C1).

[0079] Each planetary gear comprises a sun gear (S1-S5), a planet carrier (PC1-PC5), a planet gear (CA1-CA5) and a ring gear (R1-R5); the ring gears are coaxially distributed with the sun gears, the planet gears are respectively installed on the planet carriers through planet shafts and bearings, and each planet gear is internally engaged with the ring gear of the same planetary gear and externally engaged with the sun gear of the same planetary gear.

[0080] The five planetary gears are distributed in parallel from left to right, and the five sun gears, the input shaft IN and the output shaft OUT are coaxially arranged.

[0081] In the application, the power shift gearbox for the traction type engineering machine comprises five planetary gears, five brakes and a clutch, the planetary gears are all single-planet simple planetary gears, there are four forward gears and four reverse gears, the transmission ratio is uniformly distributed and the step ratio is small, the maximum traction power can be fully exerted in the working condition, and the production efficiency of the whole machine is improved. The five brakes and the clutch are all multi-plate friction control structures, the piston is pushed by hydraulic oil to brake, four forward gears and four reverse gears are realized, the step ratio of the transmission ratio of each gear in forward or reverse is in the range of 1.2-1.8, the power shift gearbox has the advantages of many gears, good power shift smoothness and compact structure, and is suitable for the tracked traction type engineering machine.

[0082] Embodiment 2: A traction type engineering machine comprising the power shift gearbox for the traction type engineering machine in embodiment 1.

[0083] In some embodiments, the traction type engineering machine can be a bulldozer.

[0084] The above only describes the preferred embodiments of the application, and it should be noted that those skilled in the art can make several improvements and refinements without departing from the principles of the application, and these improvements and refinements should also be considered as the protection scope of the application.

Claims

1. A powershift gearbox comprising an input shaft and an output shaft, characterized in that, The first planetary row and the second planetary row are arranged in sequence on the input shaft; the third planetary row, the fourth planetary row, the fifth planetary row and the first clutch are arranged in sequence on the output shaft; the first planetary row is provided with a reverse brake, the second planetary row is provided with a forward brake, the third planetary row is provided with a third brake, the fourth planetary row is provided with a fourth brake, and the fifth planetary row is provided with a second brake; The first planetary row comprises a first sun gear, a first carrier, a first planetary gear and a first ring gear, the first planetary gear is movably mounted on the first carrier, the first ring gear is engaged with the first planetary gear, the first planetary gear is engaged with the first sun gear, and the first carrier is braked by the reverse brake; The second planetary row comprises a second sun gear, a second carrier, a second planetary gear and a second ring gear, the second planetary gear is movably mounted on the second carrier, the second ring gear is engaged with the second planetary gear, the second planetary gear is engaged with the second sun gear, and the second ring gear is braked by the forward brake; The third planetary row comprises a third sun gear, a third carrier, a third planetary gear and a third ring gear, the third planetary gear is movably mounted on the third carrier, the third ring gear is engaged with the third planetary gear, the third planetary gear is engaged with the third sun gear, and the third ring gear is braked by the third brake; The fourth planetary row comprises a fourth sun gear, a fourth carrier, a fourth planetary gear and a fourth ring gear, the fourth planetary gear is movably mounted on the fourth carrier, the fourth ring gear is engaged with the fourth planetary gear, the fourth planetary gear is engaged with the fourth sun gear, and the fourth ring gear is braked by the fourth brake; The fifth planetary row comprises a fifth sun gear, a fifth carrier, a fifth planetary gear and a fifth ring gear, the fifth planetary gear is movably mounted on the fifth carrier, the fifth ring gear is engaged with the fifth planetary gear, the fifth planetary gear is engaged with the fifth sun gear, and the fifth ring gear is braked by the second brake; The inner hub of the first clutch is fixedly connected with the output shaft, and the outer hub of the first clutch is fixedly connected with the fifth ring gear; The first sun gear and the second sun gear are connected with the input shaft; the third sun gear, the fourth sun gear and the fifth sun gear are fixedly connected with the output shaft; the first ring gear is fixedly connected with the second carrier; the second carrier is fixedly connected with the third carrier, the third ring gear is fixedly connected with the fourth carrier, and the fourth ring gear is fixedly connected with the fifth carrier.

2. The powershift gearbox according to claim 1, characterized in that The forward brake and the reverse brake are direction control clutches, and the first clutch, the second brake, the third brake and the fourth brake are gear control clutches; the forward gear is realized by engaging the forward brake, the reverse gear is realized by engaging the reverse brake, the first gear is realized by engaging the first clutch, the second gear is realized by engaging the second brake, the third gear is realized by engaging the third brake, and the fourth gear is realized by engaging the fourth brake.

3. The powershift gearbox according to claim 1, characterized in that The forward gear brake is engaged with the first clutch simultaneously to realize the first forward gear; the forward gear brake is engaged with the second gear brake simultaneously to realize the second forward gear; the forward gear brake is engaged with the third gear brake simultaneously to realize the third forward gear; the forward gear brake is engaged with the fourth gear brake simultaneously to realize the fourth forward gear; the reverse gear brake is engaged with the first clutch simultaneously to realize the first reverse gear; the reverse gear brake is engaged with the second gear brake simultaneously to realize the second reverse gear; the reverse gear brake is engaged with the third gear brake simultaneously to realize the third reverse gear; the reverse gear brake is engaged with the fourth gear brake simultaneously to realize the fourth reverse gear; the step ratio of each gear transmission ratio is 1.2-1.

8.

4. The powershift gearbox of claim 1, wherein, The forward gear brake is engaged with the first clutch simultaneously to realize the first forward gear; the forward gear brake is engaged with the second gear brake simultaneously to realize the second forward gear; the forward gear brake is engaged with the third gear brake simultaneously to realize the third forward gear; the forward gear brake is engaged with the fourth gear brake simultaneously to realize the fourth forward gear; the reverse gear brake is engaged with the first clutch simultaneously to realize the first reverse gear; the reverse gear brake is engaged with the second gear brake simultaneously to realize the second reverse gear; the reverse gear brake is engaged with the third gear brake simultaneously to realize the third reverse gear; the reverse gear brake is engaged with the fourth gear brake simultaneously to realize the fourth reverse gear; the step ratio of each gear transmission ratio is 1.2-1.

8.

5. The powershift gearbox according to claim 1, characterized in that The forward gear brake is engaged with the first clutch simultaneously to realize the first forward gear; the forward gear brake is engaged with the second gear brake simultaneously to realize the second forward gear; the forward gear brake is engaged with the third gear brake simultaneously to realize the third forward gear; the forward gear brake is engaged with the fourth gear brake simultaneously to realize the fourth forward gear; the reverse gear brake is engaged with the first clutch simultaneously to realize the first reverse gear; the reverse gear brake is engaged with the second gear brake simultaneously to realize the second reverse gear; the reverse gear brake is engaged with the third gear brake simultaneously to realize the third reverse gear; the reverse gear brake is engaged with the fourth gear brake simultaneously to realize the fourth reverse gear; the step ratio of each gear transmission ratio is 1.2-1.

8. The forward gear brake is engaged with the first clutch simultaneously to realize the first forward gear; the forward gear brake is engaged with the second gear brake simultaneously to realize the second forward gear; the forward gear brake is engaged with the third gear brake simultaneously to realize the third forward gear; the forward gear brake is engaged with the fourth gear brake simultaneously to realize the fourth forward gear; the reverse gear brake is engaged with the first clutch simultaneously to realize the first reverse gear; the reverse gear brake is engaged with the second gear brake simultaneously to realize the second reverse gear; the reverse gear brake is engaged with the third gear brake simultaneously to realize the third reverse gear; the reverse gear brake is engaged with the fourth gear brake simultaneously to realize the fourth reverse gear; the step ratio of each gear transmission ratio is 1.2-1.

8. The forward gear brake is engaged with the first clutch simultaneously to realize the first forward gear; the forward gear brake is engaged with the second gear brake simultaneously to realize the second forward gear; the forward gear brake is engaged with the third gear brake simultaneously to realize the third forward gear; the forward gear brake is engaged with the fourth gear brake simultaneously to realize the fourth forward gear; the reverse gear brake is engaged with the first clutch simultaneously to realize the first reverse gear; the reverse gear brake is engaged with the second gear brake simultaneously to realize the second reverse gear; the reverse gear brake is engaged with the third gear brake simultaneously to realize the third reverse gear; the reverse gear brake is engaged with the fourth gear brake simultaneously to realize the fourth reverse gear; the step ratio of each gear transmission ratio is 1.2-1.

8. The forward gear brake is engaged with the first clutch simultaneously to realize the first forward gear; the forward gear brake is engaged with the second gear brake simultaneously to realize the second forward gear; the forward gear brake is engaged with the third gear brake simultaneously to realize the third forward gear; the forward gear brake is engaged with the fourth gear brake simultaneously to realize the fourth forward gear; the reverse gear brake is engaged with the first clutch simultaneously to realize the first reverse gear; the reverse gear brake is engaged with the second gear brake simultaneously to realize the second reverse gear; the reverse gear brake is engaged with the third gear brake simultaneously to realize the third reverse gear; the reverse gear brake is engaged with the fourth gear brake simultaneously to realize the fourth reverse gear; the step ratio of each gear transmission ratio is 1.2-1.

8.

6. The powershift gearbox of claim 1, wherein, The forward gear brake and the third gear brake are simultaneously engaged to fix the second ring gear and the third ring gear respectively, the second sun gear rotates with the input shaft at the same direction and speed through the spline connection; in the second planetary gear set, the second sun gear inputs power, the second carrier and the third carrier rotate with the input shaft due to the fixed second ring gear by the forward gear brake; in the third planetary gear set, the third carrier inputs power, the third sun gear and the third ring gear output power, the third sun gear is connected with the output shaft to drive the output shaft to rotate, and the third ring gear drives the fourth carrier to rotate; in the fourth planetary gear set, the fourth carrier inputs power, the fourth sun gear outputs power due to the fixed fourth ring gear by the fourth gear brake; finally, the third sun gear and the fourth sun gear jointly output power to the output shaft to realize the forward four gear.

7. The powershift gearbox of claim 1, wherein, The forward gear brake and the fourth gear brake are simultaneously engaged to fix the second ring gear and the fourth ring gear respectively, the second sun gear rotates with the input shaft at the same direction and speed through the spline connection; in the second planetary gear set, the second sun gear inputs power, the second carrier and the third carrier rotate with the input shaft due to the fixed second ring gear by the forward gear brake; in the third planetary gear set, the third carrier inputs power, the third sun gear and the third ring gear output power, the third sun gear is connected with the output shaft to drive the output shaft to rotate, and the third ring gear drives the fourth carrier to rotate; in the fourth planetary gear set, the fourth carrier inputs power, the fourth sun gear outputs power due to the fixed fourth ring gear by the fourth gear brake; finally, the third sun gear and the fourth sun gear jointly output power to the output shaft to realize the forward four gear.

8. The powershift gearbox of claim 1, wherein, The reverse gear brake and the first clutch are simultaneously engaged to fix the first carrier and connect the fifth ring gear and the output shaft as a whole, the first sun gear rotates with the input shaft at the same direction and speed through the spline connection; in the first planetary gear set, the first sun gear inputs power, the first ring gear and the first sun gear rotate in opposite directions and output power due to the fixed first carrier by the reverse gear brake, and the third carrier is driven to rotate; in the third planetary gear set, the third carrier inputs power, the third sun gear and the third ring gear output power, the third sun gear is connected with the output shaft to drive the output shaft to rotate, and the third ring gear drives the fourth carrier to rotate; in the fourth planetary gear set, the fourth carrier inputs power, the fourth sun gear and the fourth ring gear output power, the fourth sun gear is connected with the output shaft to drive the output shaft to rotate, and the fourth ring gear drives the fifth carrier to rotate; in the fifth planetary gear set, the fifth carrier inputs power, the fifth sun gear and the fifth ring gear jointly output power due to the fixed fifth ring gear and the output shaft as a whole by the first clutch; finally, power is output to the output shaft through the third sun gear, the fourth sun gear, the fifth sun gear and the fifth ring gear to realize the reverse one gear.

9. The powershift gearbox according to claim 1, characterized in that The reverse gear brake and the second gear brake are engaged at the same time, and the first planet carrier and the fifth ring gear are fixed respectively, the first sun gear and the input shaft are connected through the spline, and rotate in the same direction and at the same speed; in the first planetary gear set, the first sun gear inputs power, the first ring gear rotates reversely with the first sun gear and outputs power, and drives the third planet carrier to rotate at the same time; in the third planetary gear set, the third planet carrier inputs power, the third sun gear and the third ring gear output power, the third sun gear is connected with the output shaft, drives the output shaft to rotate, and the third ring gear drives the fourth planet carrier to rotate; in the fourth planetary gear set, the fourth planet carrier inputs power, the fourth sun gear and the fourth ring gear output power, the fourth sun gear is connected with the output shaft, drives the output shaft to rotate, and the fourth ring gear drives the fifth planet carrier to rotate; In the fifth planetary gear set, the second gear brake is engaged to fix the fifth ring gear, and the fifth sun gear outputs power; finally, the third sun gear, the fourth sun gear and the fifth sun gear jointly output power to the output shaft, and reverse two gears are realized.

10. The powershift transmission of claim 1, wherein, The reverse gear brake and the third gear brake are engaged at the same time, and the first planet carrier and the third ring gear are fixed respectively, the first sun gear and the input shaft are connected through the spline, and rotate in the same direction and at the same speed; in the first planetary gear set, the first sun gear inputs power, the first ring gear rotates reversely with the first sun gear and outputs power, and drives the third planet carrier to rotate at the same time; in the third planetary gear set, the third planet carrier inputs power, the third ring gear is fixed due to the engagement of the third gear brake, and the third sun gear outputs power; finally, the third sun gear outputs power to the output shaft, and reverse three gears are realized.

11. The powershift gearbox according to claim 1, characterized in that The reverse gear brake and the fourth gear brake are engaged at the same time, and the first planet carrier and the fourth ring gear are fixed respectively, the first sun gear and the input shaft are connected through the spline, and rotate in the same direction and at the same speed; in the first planetary gear set, the first sun gear inputs power, the first ring gear rotates reversely with the first sun gear and outputs power, and drives the third planet carrier to rotate at the same time; in the third planetary gear set, the third planet carrier inputs power, the third sun gear and the third ring gear output power, the third sun gear is connected with the output shaft, drives the output shaft to rotate, and the third ring gear drives the fourth planet carrier to rotate; in the fourth planetary gear set, the fourth planet carrier inputs power, the fourth ring gear is fixed due to the engagement of the fourth gear brake, and the fourth sun gear outputs power; finally, the third sun gear and the fourth sun gear jointly output power to the output shaft, and reverse four gears are realized.

12. The powershift gearbox of claim 1, wherein, The input shaft, the first sun gear, the second sun gear, the third sun gear, the fourth sun gear, the fifth sun gear and the output shaft are coaxially arranged.

13. The powershift gearbox of claim 1, wherein, The ratio of the number of teeth of the first ring gear to the number of teeth of the first sun gear is 2.529; The ratio of the number of teeth of the second ring gear to the number of teeth of the second sun gear is 2.143; The ratio of the number of teeth of the third ring gear to the number of teeth of the third sun gear is 2.143; The ratio of the number of teeth of the fourth ring gear to the number of teeth of the fourth sun gear is 1.824; The ratio of the number of teeth of the fifth ring gear to the number of teeth of the fifth sun gear is 1.

824.

14. The powershift gearbox according to claim 13, characterized in that The transmission ratio range of the first forward gear is 3.14, the transmission ratio range of the second forward gear is 2.25, the transmission ratio range of the third forward gear is 1.76, and the transmission ratio range of the fourth forward gear is 1.00; the transmission ratio range of the first reverse gear is 2.53, the transmission ratio range of the second reverse gear is 1.81, the transmission ratio range of the third reverse gear is 1.42, and the transmission ratio range of the fourth reverse gear is 0.

80.

15. The powershift gearbox according to claim 14, characterized in that The step ratio of the first forward gear to the second forward gear is 1.40, the step ratio of the second forward gear to the third forward gear is 1.28, and the step ratio of the third forward gear to the fourth forward gear is 1.76; the step ratio of the first reverse gear to the second reverse gear is 1.40, the step ratio of the second reverse gear to the third reverse gear is 1.28, and the step ratio of the third reverse gear to the fourth reverse gear is 1.

76.

16. The powershift gearbox according to any one of claims 1 to 15, characterized in that The reverse gear brake, the forward gear brake, the third gear brake, the fourth gear brake, the second gear brake, and the first clutch are all multi-plate friction control structures.

17. A tractor-type construction machine characterized by comprising: A power shift transmission comprising any one of claims 1 to 16.

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