Power shifting gearbox and tractor

Abstract

The invention discloses a power shifting gearbox and a tractor, a first gear on a first shaft and a second gear on a second shaft in a main transmission are meshed to form at least two first gear pairs, and main clutches are in one-to-one correspondence with the first gear pairs; and the other main clutches are disconnected from the corresponding first gear pairs, so that gear shifting is carried out by selectively combining one of the main clutches. In addition, due to the fact that a third gear on a third shaft and a second gear on a fourth shaft in the auxiliary speed change are meshed to form at least two second gear pairs, and auxiliary clutches correspond to the second gear pairs in a one-to-one mode, when one auxiliary clutch is combined with the corresponding second gear pair, other auxiliary clutches are disconnected with the corresponding second gear pairs, and the auxiliary speed change is achieved. And gear shifting is carried out by selecting and combining one of the auxiliary clutches. Therefore, according to the power gear shifting gearbox, multi-gear switching can be achieved under the condition that power is not interrupted, and the working efficiency can be improved.

Description

Technical Field

[0001] The present application relates to the technical field of power transmission, and in particular to a power shift transmission and a tractor. Background Art

[0002] The operating conditions of tractors are relatively complex. According to different operating conditions, the gearbox needs to be switched to the corresponding gear to give full play to the operating advantages of the tractor. The existing tractor gearbox has various shifting modes, such as gear sliding shifting or clutch sleeve shifting, but to achieve multi-gear switching, most of them need to cut off the power, and the shifting efficiency is low, which affects the operating efficiency. Summary of the invention

[0003] The purpose of the present application is to provide a power shift transmission and a tractor, which can realize multi-gear switching without interrupting power, thereby helping to improve working efficiency.

[0004] The embodiments of the present application can be implemented as follows:

[0005] In a first aspect, the present invention provides a power shift transmission, comprising:

[0006] A main transmission, comprising a first shaft, a second shaft and at least two main clutches, wherein the first shaft is parallel to the second shaft, the first shaft is used to connect to an engine, at least two first gears are arranged on the first shaft, and a main transmission output gear and at least two second gears are arranged on the second shaft; the first gears and the second gears are meshed one-to-one to form at least two first gear pairs; the main clutches correspond one-to-one to the first gear pairs, and when one main clutch is engaged with a corresponding first gear pair, the other main clutches are disconnected from their respective corresponding first gear pairs;

[0007] The auxiliary transmission is located on the side of the main transmission away from the engine, and the auxiliary transmission includes a third shaft, a fourth shaft and at least two auxiliary clutches. The third shaft is parallel to the fourth shaft, and the fourth shaft is concentric with the second shaft. The third shaft is provided with an auxiliary transmission input gear and at least two third gears, and the fourth shaft is provided with at least two fourth gears. The auxiliary transmission input gear is meshed with the main transmission output gear. The third gear is meshed with the fourth gear in a one-to-one correspondence to form at least two second gear pairs. The auxiliary clutches are in a one-to-one correspondence with the second gear pairs. When one auxiliary clutch is combined with a corresponding second gear pair, the other auxiliary clutches are disconnected from their respective corresponding second gear pairs.

[0008] In an optional embodiment, at least one main clutch is respectively provided on the first shaft and the second shaft.

[0009] In an optional embodiment, there are two main clutches on the first shaft, and a first gear is located between the two main clutches.

[0010] In an optional embodiment, there are two main clutches on the second shaft, and a second gear is located between the two main clutches.

[0011] In an optional embodiment, all the first gears include a first gear driving gear, a second gear driving gear, a third gear driving gear and a fourth gear driving gear;

[0012] The entire second gear includes a first-gear driven gear, a second-gear driven gear, a third-gear driven gear and a fourth-gear driven gear;

[0013] The first gear driven gear meshes with the first gear driving gear, the second gear driven gear meshes with the second gear driving gear, the third gear driven gear meshes with the third gear driving gear, and the fourth gear driven gear meshes with the fourth gear driving gear;

[0014] The main clutch on the first shaft includes a second-gear clutch and a third-gear clutch, wherein the second-gear clutch can be selectively combined with the second-gear driving gear, and the third-gear clutch can be selectively combined with the third-gear driving gear;

[0015] The main clutch on the second shaft includes a first-gear clutch and a fourth-gear clutch. The first-gear clutch can be selectively combined with the first-gear driven gear, and the fourth-gear clutch can be selectively combined with the fourth-gear driven gear.

[0016] In an optional embodiment, the first gear driving gear, the fourth gear driving gear, the inner gear ring of the second gear clutch and the inner gear ring of the third gear clutch are respectively rigidly connected to the first shaft;

[0017] The second gear driving gear and the third gear driving gear are respectively sleeved with the first shaft;

[0018] The main transmission output gear, the second gear driven gear, the third gear driven gear, the inner gear ring of the first gear clutch and the inner gear ring of the fourth gear clutch are rigidly connected to the second shaft respectively;

[0019] The first-gear driven gear and the fourth-gear driven gear are respectively sleeved with the second shaft.

[0020] In an optional embodiment, the fourth gear driving gear is located between the second gear clutch and the third gear clutch, and the outer gear ring of the second gear clutch, the outer gear ring of the third gear clutch, the fourth gear driving gear and the first shaft are connected as a whole.

[0021] In an optional embodiment, the second gear driven gear is located between the first gear clutch and the fourth gear clutch, and the outer gear ring of the first gear clutch, the outer gear ring of the fourth gear clutch, the second gear driven gear and the second shaft are connected as a whole.

[0022] In an optional embodiment, at least one auxiliary clutch is respectively provided on the third shaft and the fourth shaft.

[0023] In an optional embodiment, there are two auxiliary clutches on the third shaft, and a third gear is located between the two auxiliary clutches.

[0024] In an optional embodiment, there are two auxiliary clutches on the fourth shaft, and a fourth gear is located between the two auxiliary clutches.

[0025] In an optional embodiment, all third gears include an S gear driving gear, an H gear driving gear, an M gear driving gear and an L gear driving gear;

[0026] All fourth gears include an S gear driven gear, an H gear driven gear, an M gear driven gear and an L gear driven gear;

[0027] The S gear driving gear meshes with the S gear driven gear, the H gear driving gear meshes with the H gear driven gear, the M gear driving gear meshes with the M gear driven gear, and the L gear driving gear meshes with the L gear driven gear;

[0028] The auxiliary clutch on the third shaft includes an S gear clutch and an M gear clutch, wherein the S gear clutch can be selectively combined with the S gear driving gear, and the M gear clutch can be selectively combined with the M gear driving gear;

[0029] The auxiliary clutch on the fourth shaft includes an H gear clutch and an L gear clutch. The H gear clutch can be selectively combined with the H gear driven gear, and the L gear clutch can be selectively combined with the L gear driven gear.

[0030] In an optional embodiment, the auxiliary transmission input gear, the H gear driving gear, the L gear driving gear, the inner gear ring of the S gear clutch and the inner gear ring of the M gear clutch are rigidly connected to the third shaft respectively;

[0031] The S gear driving gear and the M gear driving gear are respectively sleeved with the third shaft;

[0032] The S gear driven gear, the M gear driven gear, the inner gear ring of the H gear clutch and the inner gear ring of the L gear clutch are rigidly connected to the fourth shaft respectively;

[0033] The H gear driven gear and the L gear driven gear are respectively sleeved with the fourth shaft.

[0034] In an optional embodiment, the H gear driving gear is located between the S gear clutch and the M gear clutch, and the outer gear ring of the S gear clutch, the outer gear ring of the M gear clutch, the H gear driving gear and the third shaft are connected as a whole;

[0035] In an optional embodiment, the H gear driven gear is located between the H gear clutch and the L gear clutch, and the outer gear ring of the H gear clutch, the outer gear ring of the L gear clutch, the H gear driven gear and the fourth shaft are connected as a whole.

[0036] In an optional embodiment, the power shift transmission further comprises a PTO shaft, wherein the PTO shaft is concentric with the first shaft.

[0037] In an optional embodiment, the third shaft is a hollow transmission shaft, the third shaft is concentric with the first shaft, and the PTO shaft passes through the third shaft.

[0038] In an optional embodiment, the third axis is a solid axis, and the third axis is parallel to the first axis.

[0039] In an optional embodiment, the main transmission further includes a reverse gear shaft parallel to the first shaft, and a reverse gear idler, a reverse gear clutch and a reverse gear driving gear disposed on the reverse gear shaft;

[0040] All of the first gears include a first gear driving gear, and the first gear driving gear is meshed with the reverse gear idler gear;

[0041] All of the second gears include a reverse gear driven gear, and the reverse gear driving gear is meshed with the reverse gear driven gear;

[0042] The reverse clutch can be selectively engaged with the reverse driving gear.

[0043] In an optional embodiment, the first gear driving gear is rigidly connected to the first shaft;

[0044] The reverse idler gear and the inner gear ring of the reverse clutch are rigidly connected to the reverse shaft respectively;

[0045] The reverse gear driving gear is sleeved with the reverse gear shaft;

[0046] The reverse gear driven gear is rigidly connected to the second shaft.

[0047] In an optional implementation, the first shaft, the second shaft and the reverse gear shaft are spatially distributed in a triangular shape.

[0048] In an optional embodiment, a torsional vibration damper is provided at one end of the first shaft, and the torsional vibration damper is used to be connected to a flywheel of the engine.

[0049] In a second aspect, the present invention provides a tractor comprising the power shift transmission as described in any one of the aforementioned embodiments.

[0050] Compared with the prior art, the beneficial effects of the embodiments of the present application include, for example:

[0051] Since the first gear on the first shaft and the second gear on the second shaft in the main transmission mesh to form at least two first gear pairs, and the main clutch corresponds to the first gear pair one by one, when a main clutch is combined with a first gear pair, the other main clutches are disconnected from the first gear pairs corresponding to each other, so that the gear shifting is performed by selecting one of the main clutches to be combined, and the power is not interrupted during the gear shifting process. In addition, since the third gear on the third shaft and the second gear on the fourth shaft in the auxiliary transmission mesh to form at least two second gear pairs, and the auxiliary clutch corresponds to the second gear pair one by one, when a auxiliary clutch is combined with a corresponding second gear pair, the other auxiliary clutches are disconnected from the second gear pairs corresponding to each other, so that the gear shifting is performed by selecting one of the auxiliary clutches to be combined, and the power is not interrupted during the gear shifting process. Therefore, the power shift transmission of this embodiment can realize multi-gear switching without interrupting the power, which is conducive to improving the working efficiency.

[0052] In addition, since the auxiliary transmission is located on the side of the main transmission away from the engine, the first shaft and the second shaft are arranged in parallel, the third shaft and the fourth shaft are arranged in parallel, and the fourth shaft is concentric or parallel to the second shaft, the structure of the entire gearbox can be made more compact. BRIEF DESCRIPTION OF THE DRAWINGS

[0053] In order to more clearly illustrate the specific implementation methods of the present application or the technical solutions in the prior art, the drawings required for use in the specific implementation methods or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some implementation methods of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0054] Figure 1 This is a structural principle diagram of a power shift gearbox in one embodiment of the present application;

[0055] Figure 2 for Figure 1 The spatial layout diagram of each axis;

[0056] Figure 3 This is a structural principle diagram of a power shift gearbox in another embodiment of the present application;

[0057] Figure 4 for Figure 3 The spatial layout diagram of each axis;

[0058] Figure 5 This is a structural principle diagram of a power shift transmission in another embodiment of the present application;

[0059] Figure 6 This is a structural schematic diagram of a power shift transmission in other embodiments of the present application.

[0060] Icons: M-main gear; S-secondary gear; S1-first shaft; S2-second shaft; S3-third shaft; S4-fourth shaft; SR-reverse gear shaft; SPTO-PTO shaft; ZR-reverse gear idler; CR-reverse gear clutch; ZR1-reverse gear driving gear; Z11-first gear driving gear; Z21-second gear driving gear; C2-second gear clutch; Z41-fourth gear driving gear; C3-third gear clutch; Z31-third gear driving gear; Z12-first gear passive gear; C1-first gear clutch; Z22-second gear passive gear; C4- Fourth gear clutch; Z42-fourth gear passive gear; Z32-third gear passive gear; ZR2-reverse gear passive gear; ZM-main gear output gear; ZS-secondary gear input gear; ZS1-S gear driving gear; CS-S gear clutch; ZH1-H gear driving gear; CM-M gear clutch; ZM1-M gear driving gear; ZL1-L gear driving gear; ZS2-S gear passive gear; ZH2-H gear passive gear; CH-H gear clutch; ZM2-M gear passive gear; CL-L gear clutch; ZL2-L gear passive gear. DETAILED DESCRIPTION

[0061] In order to make the purpose, technical solution and advantages of the embodiments of the present application clearer, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are part of the embodiments of the present application, rather than all the embodiments. The components of the embodiments of the present application described and shown in the drawings here can be arranged and designed in various different configurations.

[0062] Therefore, the following detailed description of the embodiments of the present application provided in the accompanying drawings is not intended to limit the scope of the present application for which protection is sought, but merely represents selected embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in the field without creative work are within the scope of protection of the present application.

[0063] It should be noted that similar reference numerals and letters denote similar items in the following drawings, and therefore, once an item is defined in one drawing, further definition and explanation thereof is not required in subsequent drawings.

[0064] In the description of the present application, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, or the positions or positional relationships in which the product of the application is usually placed when in use. They are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific position, be constructed and operated in a specific position, and therefore cannot be understood as a limitation on the present application. In addition, the terms "first", "second", "third", etc. are only used to distinguish the description, and cannot be understood as indicating or implying relative importance.

[0065] In addition, the terms "horizontal", "vertical", "overhanging" and the like do not mean that the components are required to be absolutely horizontal or overhanging, but can be slightly tilted. For example, "horizontal" only means that its direction is more horizontal than "vertical", and does not mean that the structure must be completely horizontal, but can be slightly tilted.

[0066] In the description of this application, it should also be noted that, unless otherwise clearly specified and limited, the terms "set", "install", "connect", and "connect" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two elements. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0067] The gearbox plays an extremely important role in the vehicle industry. The gearbox's structural design, performance parameters, and functional types are all critical to the operation of the vehicle. Tractors also have high requirements for gearboxes. They need to be suitable for severe working conditions, simple to operate, reduce the driver's operation, and have a certain degree of operating comfort. There are many kinds of gearboxes used in tractors on the market, and the gear shifting mode of the gearbox determines its applicable field and operating difficulty. The gear shifting modes are mainly divided into the following types:

[0068] 1. Gear sliding type and meshing sleeve type shifting. It needs to cut off the power when shifting. The peripheral speed of the gear or meshing sleeve must be the same speed to smoothly shift gears. Its disadvantages are that it will produce impact and noise when shifting gears, which will affect the working life of the gears, the shifting time is long, and the driver's operation is easily affected. It is widely used on low-cost small tractors.

[0069] 2. Synchronous gear shifting, when shifting, it is also necessary to cut off the power and the conditions of the co-speed of related parts. Compared with the gear sliding type and meshing sleeve shifting structure, the synchronization time, impact force, noise, etc. are greatly improved. At present, most small and medium-sized domestic tractors use this structure, and the power is generally within 200 horsepower.

[0070] 3. Interval power shift, which is characterized by the combination of power shift and synchronizer shift, realizes the use of power shift in common gears, and synchronizer shift can switch more gears according to working conditions, greatly improving the working efficiency and shift comfort. It is suitable for tractors with more gears, and has a trend of gradually replacing clutch sleeves and synchronizer shift.

[0071] 4. Full power shifting, which allows shifting without interrupting power. Its characteristics greatly simplify the operation process, reduce the difficulty of operation and labor intensity, thereby improving the operating efficiency. Suitable for large tractors.

[0072] However, since tractors need to shift gears frequently in actual working conditions to achieve multi-gear switching, the engine power needs to be cut off by separating the clutch before shifting gears, and the gear shifting efficiency is low, which affects the working efficiency.

[0073] To this end, the inventor has proposed the following power shift gearbox and a tractor having the power shift gearbox after research. The gearbox is characterized by a simple structure, complete functions, low manufacturing cost, and high transmission efficiency, and can realize the functions of power shifting and power reversing without cutting off the power.

[0074] The following is combined with Figures 1 to 4 , some embodiments of the present application are described in detail. In the absence of conflict, the following embodiments and features in the embodiments can be combined with each other.

[0075] The embodiment of the present application discloses a power shift transmission, which can be applied to tractors and other vehicles, without limitation to specific usage scenarios.

[0076] The powershift transmission consists of a main transmission M and a sub-transmission S.

[0077] The main transmission M includes a first shaft S1, a second shaft S2 and at least two main clutches. The first shaft S1 and the second shaft S2 are parallel. The first shaft S1 is used to connect the engine. At least two first gears are arranged on the first shaft S1. The second shaft S2 is provided with a main transmission output gear ZM and at least two second gears. The first gears and the second gears are meshed one by one to form at least two first gear pairs. The main clutches correspond to the first gear pairs one by one. When one main clutch is engaged with a corresponding first gear pair, the other main clutches are disconnected from the corresponding first gear pairs.

[0078] The auxiliary transmission S is located on the side of the main transmission M away from the engine. The auxiliary transmission S includes a third shaft, a fourth shaft S4 and at least two auxiliary clutches. The third shaft and the fourth shaft S4 are parallel, and the fourth shaft S4 and the second shaft S2 are concentric. The third shaft is provided with an auxiliary transmission input gear ZS and at least two third gears, and the fourth shaft S4 is provided with at least two fourth gears. The auxiliary transmission input gear ZS is meshed with the main transmission output gear ZM. The third gear is meshed with the fourth gear in a one-to-one correspondence to form at least two second gear pairs. The auxiliary clutches are in a one-to-one correspondence with the second gear pairs. When one auxiliary clutch is combined with a corresponding second gear pair, the other auxiliary clutches are disconnected from their respective corresponding second gear pairs.

[0079] In this way, since the first gear on the first shaft S1 and the second gear on the second shaft S2 in the main transmission M are meshed to form at least two first gear pairs, and the main clutch corresponds to the first gear pair one by one, when a main clutch is combined with a first gear pair, the other main clutches are disconnected from the first gear pairs corresponding to each other, so that the gear shift is performed by selecting one of the main clutches to be combined, and the power is not interrupted during the gear shift process. In addition, since the third gear on the third shaft in the auxiliary transmission S and the second gear on the fourth shaft S4 are meshed to form at least two second gear pairs, and the auxiliary clutch corresponds to the second gear pair one by one, when a auxiliary clutch is combined with a corresponding second gear pair, the other auxiliary clutches are disconnected from the second gear pairs corresponding to each other, so that the gear shift is performed by selecting one of the auxiliary clutches to be combined, and the power is not interrupted during the gear shift process. Therefore, the power shift transmission of this embodiment can realize multi-gear switching without interrupting the power, which is conducive to improving the working efficiency. In addition, since the auxiliary transmission S is located on the side of the main transmission away from the engine, the first shaft S1 and the second shaft S2 are arranged in parallel, the third shaft and the fourth shaft S4 are arranged in parallel, and the fourth shaft S4 is concentric or parallel to the second shaft S2, the structure of the entire gearbox can be made more compact.

[0080] In the main transmission M, at least one main clutch is provided on the first shaft S1 and the second shaft S2, respectively. For example, there are two main clutches on the first shaft S1, and a first gear is located between the two main clutches; for example, there are two main clutches on the second shaft S2, and a second gear is located between the two main clutches. Of course, in some embodiments, at least two main clutches may be provided only on the first shaft S1; at least two main clutches may also be provided only on the second shaft S2.

[0081] Specifically, all the first gears include a first gear driving gear Z11, a second gear driving gear Z21, a third gear driving gear Z31 and a fourth gear driving gear Z41; all the second gears include a first gear passive gear Z12, a second gear passive gear Z22, a third gear passive gear Z32 and a fourth gear passive gear Z42; the first gear passive gear Z12 is meshed with the first gear driving gear Z11, the second gear passive gear Z22 is meshed with the second gear driving gear Z21, the third gear passive gear Z32 is meshed with the third gear driving gear Z31, and the fourth gear passive gear Z42 is meshed with the fourth gear driving gear Z41;

[0082] The main clutch on the first shaft S1 includes a second-gear clutch C2 and a third-gear clutch C3. The second-gear clutch C2 can be selectively combined with the second-gear driving gear Z21, and the third-gear clutch C3 can be selectively combined with the third-gear driving gear Z31; the main clutch on the second shaft S2 includes a first-gear clutch C1 and a fourth-gear clutch C4. The first-gear clutch C1 can be selectively combined with the first-gear driven gear Z12, and the fourth-gear clutch C4 can be selectively combined with the fourth-gear driven gear Z42.

[0083] Among them, the first gear driving gear Z11, the fourth gear driving gear Z41, the inner gear ring of the second gear clutch C2 and the inner gear ring of the third gear clutch C3 are respectively rigidly connected to the first shaft S1 and fixed relative to the first shaft S1 to rotate synchronously with the first shaft S1. For example, the inner gear ring of the second gear clutch C2, the fourth gear driving gear Z41, and the inner gear ring of the third gear clutch C3 are respectively integrated with the first shaft S1.

[0084] The second gear driving gear Z21 and the third gear driving gear Z31 are respectively sleeved with the first shaft S1, so they can rotate relative to the first shaft S1 when not engaged with the main clutch, and are fixed relative to the first shaft S1 when engaged with the main clutch to rotate synchronously with the first shaft S1.

[0085] The main speed output gear ZM, the second gear driven gear Z22, the third gear driven gear Z32, the inner ring gear of the first gear clutch C1 and the inner ring gear of the fourth gear clutch C4 are respectively rigidly connected to the second shaft S2, remain fixed relative to the second shaft S2, and rotate synchronously with the second shaft S2. For example, the inner ring gear of the first gear clutch C1, the second gear driven gear Z22, and the inner ring gear of the fourth gear clutch C4 are respectively integrated with the second shaft S2.

[0086] The first gear driven gear Z12 and the fourth gear driven gear Z42 are respectively sleeved with the second shaft S2, so they can rotate relative to the second shaft S2 when not engaged with the auxiliary clutch, and are fixed relative to the second shaft S2 and rotate synchronously with the second shaft S2 when engaged with the auxiliary clutch.

[0087] The fourth gear driving gear Z41 is located between the second gear clutch C2 and the third gear clutch C3, and the outer gear ring of the second gear clutch C2, the outer gear ring of the third gear clutch C3, the fourth gear driving gear Z41 and the first shaft S1 are connected as a whole. The second gear driven gear Z22 is located between the first gear clutch C1 and the fourth gear clutch C4, and the outer gear ring of the first gear clutch C1, the outer gear ring of the fourth gear clutch C4, the second gear driven gear Z22 and the second shaft S2 are connected as a whole.

[0088] In addition, the main transmission M also includes a reverse gear shaft SR parallel to the first shaft S1, and a reverse gear idler gear ZR, a reverse gear clutch CR and a reverse gear driving gear ZR1 arranged on the reverse gear shaft SR; the first gear driving gear Z11 is meshed with the reverse gear idler gear ZR; all second gears include a reverse gear driven gear ZR2, and the reverse gear driving gear ZR1 is meshed with the reverse gear driven gear ZR2; the reverse gear clutch CR can be selectively combined with the reverse gear driving gear ZR1.

[0089] Among them, the reverse idler gear ZR and the inner gear ring of the reverse clutch CR are respectively rigidly connected to the reverse shaft SR and remain fixed relative to the reverse shaft SR. For example, the inner gear ring of the reverse clutch CR and the reverse shaft SR are set as an integral structure. The reverse driving gear ZR1 is sleeved with the reverse shaft SR so that the reverse driving gear ZR1 and the reverse shaft SR can rotate relative to each other when not combined with the reverse clutch CR, and remain fixed relative to the reverse shaft SR when combined with the reverse clutch CR, and rotate synchronously with the reverse shaft SR. The first shaft S1, the second shaft S2 and the reverse shaft SR are distributed in a triangular shape in space. This makes the structure more compact, the transmission efficiency higher, simple and convenient, effectively saves space, and reduces the volume of the gearbox.

[0090] It can be understood that each gear in the main transmission M is controlled by a main clutch, and only one of the clutches can be engaged at the same time, that is, when a main clutch is engaged with a first gear pair, the other main clutches are disconnected from the corresponding first gear pair, and the reverse clutch CR is also disconnected; and when the reverse clutch CR is engaged, all the main clutches are disconnected. The first gear clutch C1, the second gear clutch C2, the third gear clutch C3 and the fourth gear clutch C4 control one forward gear respectively, forming four forward gears, and the reverse clutch CR controls the reverse gear, forming a reverse power gear, realizing 4F+1R, a total of five gears. During the gear shifting process, when one of the main clutches and a corresponding first gear pair changes from being engaged to being disconnected, the gear shifting can be achieved by engaging the other main clutches with their respective corresponding first gear pairs. For example, when the second gear clutch C2 is engaged with the second gear driving gear Z21 and is in the second gear state, if the second gear clutch C2 starts to be disconnected, the third clutch and the third gear driving gear Z31 start to be engaged, so that the power gear is switched from the second gear to the third gear. Therefore, the gear shifting can be achieved without cutting off the power.

[0091] In the auxiliary transmission S, the third shaft and the fourth shaft S4 each have at least one auxiliary clutch. For example, the third shaft S3 has two auxiliary clutches, and a third gear is located between the two auxiliary clutches; the fourth shaft S4 has two auxiliary clutches, and a fourth gear is located between the two auxiliary clutches.

[0092] Of course, in some embodiments, at least two auxiliary clutches may be provided only on the third shaft; at least two auxiliary clutches may be provided only on the fourth shaft S4.

[0093] Specifically, all the third gears include an S gear driving gear ZS1, an H gear driving gear ZH1, an M gear driving gear ZM1, and an L gear driving gear ZL1; all the fourth gears include an S gear driven gear ZS2, an H gear driven gear ZH2, an M gear driven gear ZM2, and an L gear driven gear ZL2; the S gear driving gear ZS1 is meshed with the S gear driven gear ZS2, the H gear driving gear ZH1 is meshed with the H gear driven gear ZH2, the M gear driving gear ZM1 is meshed with the M gear driven gear ZM2, and the L gear driving gear ZL1 is meshed with the L gear driven gear ZL2;

[0094] The auxiliary clutch on the third shaft includes an S gear clutch CS and an M gear clutch CM. The S gear clutch CS can be selectively combined with the S gear driving gear ZS1, and the M gear clutch CM can be selectively combined with the M gear driving gear ZM1; the auxiliary clutch on the fourth shaft S4 includes an H gear clutch CH and an L gear clutch CL. The H gear clutch CH can be selectively combined with the H gear driven gear ZH2, and the L gear clutch CL can be selectively combined with the L gear driven gear ZL2.

[0095] Among them, the auxiliary speed input gear ZS, the H gear driving gear ZH1, the L gear driving gear ZL1, the inner ring gear of the S gear clutch CS and the inner ring gear of the M gear clutch CM are respectively rigidly connected to the third shaft, remain fixed relative to the third shaft, and rotate synchronously with the third shaft. For example, the inner ring gear of the S gear clutch CS, the H gear driving gear ZH1, and the inner ring gear of the M gear clutch CM are respectively integrated with the third shaft S3.

[0096] The S gear driving gear ZS1 and the M gear driving gear ZM1 are respectively sleeved with the third shaft so as to be able to rotate relative to the third shaft when not engaged with the auxiliary clutch, and remain fixed relative to the third shaft and rotate synchronously with the third shaft when engaged with the auxiliary clutch.

[0097] The S gear driven gear ZS2, the M gear driven gear ZM2, the inner gear ring of the H gear clutch CH and the inner gear ring of the L gear clutch CL are respectively rigidly connected to the fourth shaft S4, remain fixed relative to the fourth shaft S4, and rotate synchronously with the fourth shaft S4. For example, the inner gear ring of the H gear clutch CH, the M gear driven gear ZM2 and the inner gear ring of the L gear clutch CL are respectively integrated with the fourth shaft S4.

[0098] The H gear driven gear ZH2 and the L gear driven gear ZL2 are respectively connected to the fourth shaft S4 so as to be able to rotate relative to the fourth shaft S4 when not engaged with the auxiliary clutch, and remain fixed relative to the fourth shaft S4 and rotate synchronously with the fourth shaft S4 when engaged with the auxiliary clutch.

[0099] Among them, the H gear driving gear ZH1 is located between the S gear clutch CS and the M gear clutch CM, and the outer ring gear of the S gear clutch CS, the outer ring gear of the M gear clutch CM, the H gear driving gear ZH1 and the third shaft S3 are connected as a whole; the H gear driven gear ZH2 is located between the H gear clutch CH and the L gear clutch CL, and the outer ring gear of the H gear clutch CH, the outer ring gear of the L gear clutch CL, the H gear driven gear ZH2 and the fourth shaft S4 are connected as a whole.

[0100] It can be understood that each gear in the auxiliary transmission S is controlled by a sub-clutch, and only one of the sub-clutches can be engaged at the same time, that is, when one sub-clutch is engaged with a second gear pair, the other sub-clutches are disconnected from their respective corresponding second gear pairs. The S gear clutch CS, the M gear clutch CM, the H gear clutch CH and the L gear clutch CL each control a gear, forming four gears. During the gear shifting process, when one of the sub-clutches is in a state where it is disconnected from the corresponding second gear pair, the gear shifting can be achieved by combining the other sub-clutches with their corresponding second gear pairs. For example, when the M gear clutch CM is combined with the M gear driving gear ZM1 and is in the M gear state, if the M gear clutch CM starts to disconnect, the H gear clutch CH starts to combine with the H gear driven gear ZH2 to switch the power gear from the M gear to the H gear, so that the gear shifting can be achieved without cutting off the power.

[0101] In addition, it is also necessary to note that during the operation of the power shift transmission, there is a clutch engaged in both the main transmission M and the auxiliary transmission S, that is, only one main clutch is engaged or the reverse clutch CR is engaged in the main transmission M, and only one auxiliary clutch is engaged in the auxiliary transmission S. In this way, the main transmission M can transmit the engine power to the auxiliary transmission S, and finally output it to the transmission through the fourth shaft S4 and connect to the rear axle.

[0102] The power shift transmission further comprises a PTO shaft SPTO which is concentric with the first shaft S1 and which is mainly connected to the rear axle.

[0103] Among them, reference Figure 1 and Figure 2 The third shaft is a hollow transmission shaft, the third shaft is concentric with the first shaft S1, and the PTO shaft SPTO passes through the third shaft to make the structure of the gearbox more compact.

[0104] A torsional vibration damper (X) is disposed at one end of the first shaft S1, and the torsional vibration damper (X) is used to be connected to the flywheel of the engine to ensure stable transmission of power.

[0105] Thus, the power shift gearbox of this embodiment can be used for tractors with about 250 horsepower, and its gear distribution is 16F+4R (16 forward gears, 4 reverse gears). The gearbox is characterized by simple structure, complete functions, low manufacturing cost, high transmission efficiency, and can realize the functions of power shifting and power reversing.

[0106] In addition, Figure 3 and Figure 4 In the illustrated embodiment, the third shaft is a solid shaft, and the third shaft is parallel to the first shaft S1, so that the gear position of 16F+4R can also be achieved.

[0107] exist Figures 1 to 4 In the illustrated embodiment, the outer ring of the left end bearing of the fourth shaft S4 is fixed on the second shaft S2 or the main transmission output gear ZM, so the second shaft S2 and the fourth shaft S4 are concentric at this time.

[0108] In addition, reference Figure 5 and Figure 6 The outer ring of the left end bearing of the fourth shaft S4 can also be fixed on the partition wall of the gearbox housing for support, so that the second shaft S2 and the fourth shaft S4 can be concentric or non-concentric.

[0109] In summary, power is input from the front end of the first shaft S1 and output from the rear end of the fourth shaft S4. When the forward gear is engaged, the power is transmitted through 3 pairs of gears; when the reverse gear is engaged, the power is transmitted through 4 pairs of gears, with high transmission efficiency and low loss.

[0110] It is understandable that in this embodiment, both the main clutch and the auxiliary clutch can adopt a normally separated electro-hydraulic controlled wet multi-plate clutch, and each clutch can realize the engagement and disengagement of the clutch according to the command. The following is an example in conjunction with Table 1 (gear combination table):

[0111] Table 1: Clutch combination table for each gear

[0112]

[0113] The first gear clutch C1 can be rigidly connected with the first gear driven gear Z12 according to the control command, and at this time, the second shaft S2, the first gear driven gear Z12, the first gear clutch C1 and other parts do not rotate relative to each other;

[0114] The second gear clutch C2 can be rigidly connected with the second gear driving gear Z21 according to the control command, and at this time, the first shaft S1, the second gear driving gear Z21, the second gear clutch C2 and other parts do not rotate relative to each other;

[0115] The third gear clutch C3 can be rigidly connected with the third gear driving gear Z31 according to the control command, and at this time, the first shaft S1, the third gear driving gear Z31, the third gear clutch C3 and other parts do not rotate relative to each other;

[0116] The fourth-gear clutch C4 can be rigidly connected with the fourth-gear driven gear Z42 according to the control command, and at this time, the second shaft S2, the fourth-gear driven gear Z42, the fourth-gear clutch C4 and other parts do not rotate relative to each other;

[0117] The reverse clutch CR can be rigidly connected with the reverse driving gear ZR1 according to the control command. At this time, the reverse shaft SR, the reverse driving gear ZR1, the reverse clutch CR and other parts do not rotate relative to each other.

[0118] The S gear clutch CS can be rigidly connected with the S gear driving gear ZS1 according to the control command. At this time, the third shaft S3, the S gear driving gear ZS1, the S gear clutch CS and other parts do not rotate relative to each other;

[0119] The H gear clutch CH can be rigidly connected with the H gear driven gear ZH2 according to the control command, and at this time, the fourth shaft S4, the H gear driven gear ZH2, the H gear clutch CH and other parts do not rotate relative to each other;

[0120] The M-gear clutch CM can be rigidly connected with the M-gear driving gear ZM1 according to the control command. At this time, the third shaft S3, the M-gear driving gear ZM1, the M-gear clutch CM and other parts do not rotate relative to each other;

[0121] The L gear clutch CL can be rigidly connected to the L gear driven gear ZL2 according to the control command. At this time, the fourth shaft S4, the L gear driven gear ZL2, the L gear clutch CL and other parts do not rotate relatively.

[0122] In the main transmission M and the auxiliary transmission S, each gear clutch controls a gear individually. When different clutches in the main transmission M and the auxiliary transmission S are combined, the gearbox will have different transmission ratios and form different gears, a total of 16 forward gears and 4 reverse gears. The power transmission route of each gear is explained below:

[0123] L1 gear: 1st gear clutch C1 and L gear clutch CL are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 1st gear driving gear Z11 → 1st gear driven gear Z12 → 1st gear clutch C1 → second shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → third shaft S3 → L gear driving gear ZL1 → L gear driven gear ZL2 → L gear clutch CL → fourth shaft S4 → output end.

[0124] L2 gear: 2nd gear clutch C2 and L gear clutch CL are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 2nd gear clutch C2 → 2nd gear driving gear Z21 → 2nd gear driven gear Z22 → 2nd shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → 3rd shaft S3 → L gear driving gear ZL1 → L gear driven gear ZL2 → L gear clutch CL → 4th shaft S4 → output end.

[0125] L3 gear: 3rd gear clutch C3 and L gear clutch CL are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 3rd gear clutch C3 → 3rd gear driving gear Z31 → 3rd gear driven gear Z32 → second shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → third shaft S3 → L gear driving gear ZL1 → L gear driven gear ZL2 → L gear clutch CL → fourth shaft S4 → output end.

[0126] L4 gear: 4th gear clutch C4 and L gear clutch CL are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 4th gear driving gear Z41 → 4th gear driven gear Z42 → 4th gear clutch C4 → 2nd shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → 3rd shaft S3 → L gear driving gear ZL1 → L gear driven gear ZL2 → L gear clutch CL → 4th shaft S4 → output end.

[0127] M1 gear: 1st gear clutch C1 and M gear clutch CM are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 1st gear driving gear Z11 → 1st gear passive gear Z12 → 1st gear clutch C1 → 2nd shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → 3rd shaft S3 → M gear clutch CM → M gear driving gear ZM1 → M gear passive gear ZM2 → 4th shaft S4 → output end.

[0128] M2 gear: 2nd gear clutch C2 and M gear clutch CM are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 2nd gear clutch C2 → 2nd gear driving gear Z21 → 2nd gear driven gear Z22 → 2nd shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → 3rd shaft S3 → M gear clutch CM → M gear driving gear ZM1 → M gear driven gear ZM2 → 4th shaft S4 → output end.

[0129] M3 gear: 3rd gear clutch C3 and M gear clutch CM are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 3rd gear clutch C3 → 3rd gear driving gear Z31 → 3rd gear passive gear Z32 → second shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → third shaft S3 → M gear clutch CM → M gear driving gear ZM1 → M gear passive gear ZM2 → fourth shaft S4 → output end.

[0130] M4 gear: 4th gear clutch C4 and M gear clutch CM are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 4th gear driving gear Z41 → 4th gear driven gear Z42 → 4th gear clutch C4 → 2nd shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → 3rd shaft S3 → M gear clutch CM → M gear driving gear ZM1 → M gear driven gear ZM2 → 4th shaft S4 → output end.

[0131] H1 gear: 1st gear clutch C1 and H gear clutch CH are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 1st gear driving gear Z11 → 1st gear driven gear Z12 → 1st gear clutch C1 → second shaft S2 → main speed output gear ZM → auxiliary speed input gear ZS → third shaft S3 → H gear driving gear ZH1 → H gear driven gear ZH2 → H gear clutch CH → fourth shaft S4 → output end.

[0132] H2 gear: 2nd gear clutch C2 and H gear clutch CH are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 2nd gear clutch C2 → 2nd gear driving gear Z21 → 2nd gear driven gear Z22 → 2nd shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → 3rd shaft S3 → H gear driving gear ZH1 → H gear driven gear ZH2 → H gear clutch CH → 4th shaft S4 → output end.

[0133] H3 gear: 3rd gear clutch C3 and H gear clutch CH are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 3rd gear clutch C3 → 3rd gear driving gear Z31 → 3rd gear driven gear Z32 → second shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → third shaft S3 → H gear driving gear ZH1 → H gear driven gear ZH2 → H gear clutch CH → fourth shaft S4 → output end.

[0134] H4 gear: 4th gear clutch C4 and H gear clutch CH are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 4th gear driving gear Z41 → 4th gear driven gear Z42 → 4th gear clutch C4 → 2nd shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → 3rd shaft S3 → H gear driving gear ZH1 → H gear driven gear ZH2 → H gear clutch CH → 4th shaft S4 → output end.

[0135] S1 gear: 1st gear clutch C1 and S gear clutch CS are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 1st gear driving gear Z11 → 1st gear driven gear Z12 → 1st gear clutch C1 → 2nd shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → 3rd shaft S3 → S gear clutch CS → S gear driving gear ZS1 → S gear driven gear ZS2 → 4th shaft S4 → output end.

[0136] S2 gear: 2nd gear clutch C2 and S gear clutch CS are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 2nd gear clutch C2 → 2nd gear driving gear Z21 → 2nd gear driven gear Z22 → second shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → third shaft S3 → S gear clutch CS → S gear driving gear ZS1 → S gear driven gear ZS2 → fourth shaft S4 → output end.

[0137] S3 gear: 3rd gear clutch C3 and S gear clutch CS are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 3rd gear clutch C3 → 3rd gear driving gear Z31 → 3rd gear driven gear Z32 → second shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → third shaft S3 → S gear clutch CS → S gear driving gear ZS1 → S gear driven gear ZS2 → fourth shaft S4 → output end.

[0138] S4 gear: 4th gear clutch C4 and S gear clutch CS are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → 4th gear driving gear Z41 → 4th gear driven gear Z42 → 4th gear clutch C4 → 2nd shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → 3rd shaft S3 → S gear clutch CS → S gear driving gear ZS1 → S gear driven gear ZS2 → 4th shaft S4 → output end.

[0139] RL gear: reverse clutch CR and L gear clutch CL are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → first gear driving gear Z11 → reverse gear idler ZR → reverse clutch CR → reverse gear driving gear ZR1 → reverse gear driven gear ZR2 → second shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → third shaft S3 → L gear driving gear ZL1 → L gear driven gear ZL2 → L gear clutch CL → fourth shaft S4 → output end.

[0140] RM gear: reverse clutch CR and M gear clutch CM are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → first gear driving gear Z11 → reverse gear idler ZR → reverse clutch CR → reverse gear driving gear ZR1 → reverse gear driven gear ZR2 → second shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → third shaft S3 → M gear clutch CM → M gear driving gear ZM1 → M gear driven gear ZM2 → fourth shaft S4 → output end.

[0141] RH gear: reverse clutch CR and H gear clutch CH are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → first gear driving gear Z11 → reverse gear idler ZR → reverse clutch CR → reverse gear driving gear ZR1 → reverse gear driven gear ZR2 → second shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → third shaft S3 → H gear driving gear ZH1 → H gear driven gear ZH2 → H gear clutch CH → fourth shaft S4 → output end.

[0142] RS gear: Reverse clutch CR and S gear clutch CS are engaged, and other clutches are disengaged. The engine power is transmitted along the first shaft S1 → first gear driving gear Z11 → reverse gear idler ZR → reverse clutch CR → reverse gear driving gear ZR1 → reverse gear passive gear ZR2 → second shaft S2 → main transmission output gear ZM → auxiliary transmission input gear ZS → third shaft S3 → S gear clutch CS → S gear driving gear ZS1 → S gear passive gear ZS2 → fourth shaft S4 → output end.

[0143] In addition, this embodiment also discloses a tractor, which includes the power shift transmission of the above embodiment, and thus also has corresponding structure and beneficial effects, which will not be described in detail here.

[0144] In summary, the power shift transmission and tractor disclosed in the embodiments of the present application have at least the following advantages:

[0145] 1. Simple structure, low cost, easy to disassemble and assemble;

[0146] 2. Compact distribution, effectively saving space and reducing the volume of the gearbox;

[0147] 3. Fewer transmission parts, which reduces transmission loss and improves transmission efficiency;

[0148] 4. Complete functions, realizing full power shifting and power reversing functions.

[0149] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present application, rather than to limit it. Although the present application has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present application.

Claims

1. A power shift gearbox, characterized in that: include: A main transmission (M), comprising a first shaft (S1), a second shaft (S2) and at least two main clutches, wherein the first shaft (S1) and the second shaft (S2) are parallel, the first shaft (S1) is used to connect to an engine, at least two first gears are arranged on the first shaft (S1), and a main transmission output gear (ZM) and at least two second gears are arranged on the second shaft (S2); the first gears and the second gears are meshed one by one to form at least two first gear pairs; The main clutches correspond to the first gear pairs one by one, and when one main clutch is engaged with a corresponding first gear pair, the other main clutches are disconnected from the corresponding first gear pairs; A secondary transmission (S) is located at a side of the main transmission (M) away from the engine, the secondary transmission (S) comprises a third shaft, a fourth shaft (S4) and at least two secondary clutches, the third shaft and the fourth shaft (S4) are parallel, the fourth shaft (S4) and the second shaft (S2) are concentric or parallel; the third shaft is provided with a secondary transmission input gear (ZS) and at least two third gears, the fourth shaft (S4) is provided with at least two fourth gears; the secondary transmission input gear (ZS) is meshed with the main transmission output gear (ZM); The third gear is meshed with the fourth gear in a one-to-one correspondence to form at least two second gear pairs; the auxiliary clutches are in a one-to-one correspondence with the second gear pairs, and when one auxiliary clutch is engaged with a corresponding second gear pair, the other auxiliary clutches are disconnected from their respective corresponding second gear pairs.

2. The power shift transmission according to claim 1, characterized in that: The first shaft (S1) and the second shaft (S2) are each provided with at least one main clutch.

3. The power shift transmission according to claim 2, characterized in that: The first shaft (S1) has two main clutches, and a first gear is located between the two main clutches; and / or, The second shaft (S2) has two main clutches, and a second gear is located between the two main clutches.

4. The power shift transmission according to claim 2 or 3, characterized in that: The first gears include a first gear driving gear (Z11), a second gear driving gear (Z21), a third gear driving gear (Z31) and a fourth gear driving gear (Z41); The second gears include a first gear driven gear (Z12), a second gear driven gear (Z22), a third gear driven gear (Z32) and a fourth gear driven gear (Z42); The first gear driven gear (Z12) meshes with the first gear driving gear (Z11), the second gear driven gear (Z22) meshes with the second gear driving gear (Z21), the third gear driven gear (Z32) meshes with the third gear driving gear (Z31), and the fourth gear driven gear (Z42) meshes with the fourth gear driving gear (Z41); The main clutch on the first shaft (S1) includes a second-gear clutch (C2) and a third-gear clutch (C3), wherein the second-gear clutch (C2) can be selectively combined with the second-gear driving gear (Z21), and the third-gear clutch (C3) can be selectively combined with the third-gear driving gear (Z31); The main clutch on the second shaft (S2) includes a first-gear clutch (C1) and a fourth-gear clutch (C4), wherein the first-gear clutch (C1) can be selectively combined with the first-gear driven gear (Z12), and the fourth-gear clutch (C4) can be selectively combined with the fourth-gear driven gear (Z42).

5. The power shift transmission according to claim 4, characterized in that: The first gear driving gear (Z11), the fourth gear driving gear (Z41), the inner gear ring of the second gear clutch (C2) and the inner gear ring of the third gear clutch (C3) are rigidly connected to the first shaft (S1) respectively; The second gear driving gear (Z21) and the third gear driving gear (Z31) are respectively sleeved with the first shaft (S1); The main transmission output gear (ZM), the second gear driven gear (Z22), the third gear driven gear (Z32), the inner gear ring of the first gear clutch (C1) and the inner gear ring of the fourth gear clutch (C4) are rigidly connected to the second shaft (S2) respectively; The first-gear driven gear (Z12) and the fourth-gear driven gear (Z42) are respectively sleeved with the second shaft (S2).

6. The power shift transmission according to claim 5, characterized in that: The fourth-gear driving gear (Z41) is located between the second-gear clutch (C2) and the third-gear clutch (C3), and the outer gear ring of the second-gear clutch (C2), the outer gear ring of the third-gear clutch (C3), the fourth-gear driving gear (Z41) and the first shaft (S1) are connected as a whole; and / or, The second gear driven gear (Z22) is located between the first gear clutch (C1) and the fourth gear clutch (C4), and the outer gear ring of the first gear clutch (C1), the outer gear ring of the fourth gear clutch (C4), the second gear driven gear (Z22) and the second shaft (S2) are connected as a whole.

7. The power shift transmission according to claim 1, characterized in that: The third shaft and the fourth shaft (S4) are each provided with at least one auxiliary clutch.

8. The power shift transmission according to claim 7, characterized in that: The third shaft (S3) has two auxiliary clutches, and a third gear is located between the two auxiliary clutches; and / or, The fourth shaft (S4) has two auxiliary clutches, and a fourth gear is located between the two auxiliary clutches.

9. The power shift transmission according to claim 7 or 8, characterized in that: All third gears include an S gear driving gear (ZS1), an H gear driving gear (ZH1), an M gear driving gear (ZM1) and an L gear driving gear (ZL1); The fourth gears include an S-speed driven gear (ZS2), an H-speed driven gear (ZH2), an M-speed driven gear (ZM2) and an L-speed driven gear (ZL2); The S gear driving gear (ZS1) meshes with the S gear driven gear (ZS2), the H gear driving gear (ZH1) meshes with the H gear driven gear (ZH2), the M gear driving gear (ZM1) meshes with the M gear driven gear (ZM2), and the L gear driving gear (ZL1) meshes with the L gear driven gear (ZL2); The auxiliary clutch on the third shaft includes an S gear clutch (CS) and an M gear clutch (CM), wherein the S gear clutch (CS) can be selectively combined with the S gear driving gear (ZS1), and the M gear clutch (CM) can be selectively combined with the M gear driving gear (ZM1); The auxiliary clutch on the fourth shaft (S4) includes an H gear clutch (CH) and an L gear clutch (CL), wherein the H gear clutch (CH) can be selectively combined with the H gear driven gear (ZH2), and the L gear clutch (CL) can be selectively combined with the L gear driven gear (ZL2).

10. The power shift transmission according to claim 9, characterized in that: The auxiliary speed change input gear (ZS), the H gear driving gear (ZH1), the L gear driving gear (ZL1), the inner gear ring of the S gear clutch (CS) and the inner gear ring of the M gear clutch (CM) are rigidly connected to the third shaft respectively; The S gear driving gear (ZS1) and the M gear driving gear (ZM1) are respectively sleeved with the third shaft; The S gear driven gear (ZS2), the M gear driven gear (ZM2), the inner gear ring of the H gear clutch (CH) and the inner gear ring of the L gear clutch (CL) are rigidly connected to the fourth shaft (S4) respectively; The H gear driven gear (ZH2) and the L gear driven gear (ZL2) are respectively sleeved with the fourth shaft (S4).

11. The power shift transmission according to claim 10, characterized in that: The H gear driving gear (ZH1) is located between the S gear clutch (CS) and the M gear clutch (CM), and the outer gear ring of the S gear clutch (CS), the outer gear ring of the M gear clutch (CM), the H gear driving gear (ZH1) and the third shaft (S3) are connected as a whole; and / or, The H gear driven gear (ZH2) is located between the H gear clutch (CH) and the L gear clutch (CL), and the outer ring gear of the H gear clutch (CH), the outer ring gear of the L gear clutch (CL), the H gear driven gear (ZH2) and the fourth shaft (S4) are connected as a whole.

12. The power shift transmission according to claim 1, characterized in that: The power shift transmission further comprises a PTO shaft (SPTO), which is concentric with the first shaft (S1).

13. The power shift transmission according to claim 12, characterized in that: The third shaft is a hollow transmission shaft, the third shaft is concentric with the first shaft (S1), and the PTO shaft (SPTO) is passed through the third shaft.

14. The power shift transmission according to claim 12, characterized in that: The third axis is a solid axis, and the third axis is parallel to the first axis (S1).

15. The power shift transmission according to claim 1, characterized in that: The main transmission (M) further comprises a reverse gear shaft (SR) parallel to the first shaft (S1), and a reverse gear idler (ZR), a reverse gear clutch (CR) and a reverse gear driving gear (ZR1) arranged on the reverse gear shaft (SR); All the first gears include a first gear driving gear (Z11), and the first gear driving gear (Z11) is meshed with the reverse gear idler gear (ZR); All the second gears include a reverse gear driven gear (ZR2), and the reverse gear driving gear (ZR1) is meshed with the reverse gear driven gear (ZR2); The reverse clutch (CR) can be selectively engaged with the reverse driving gear (ZR1).

16. The power shift transmission according to claim 15, characterized in that: The first gear driving gear (Z11) is rigidly connected to the first shaft (S1); The reverse idler gear (ZR) and the inner gear ring of the reverse clutch (CR) are rigidly connected to the reverse shaft (SR) respectively; The reverse gear driving gear (ZR1) is sleeve-connected with the reverse gear shaft (SR); The reverse gear driven gear (ZR2) is rigidly connected to the second shaft (S2).

17. The power shift transmission according to claim 15, characterized in that: The first shaft (S1), the second shaft (S2) and the reverse shaft (SR) are spatially distributed in a triangular shape.

18. The power shift transmission according to claim 1, characterized in that: A torsional vibration damper (X) is arranged at one end of the first shaft (S1), and the torsional vibration damper (X) is used to be connected to a flywheel of an engine.

19. A tractor, characterized in that: A power shift transmission comprising any one of claims 1-18.

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