阅读说明：本技术 一种装载机液压机械分流传动装置 (Hydraulic mechanical shunt transmission device of loading machine ) 是由 曲立伟 马文星 王忠山 于 2021-03-29 设计创作，主要内容包括：本发明公开了一种装载机液压机械分流传动装置,其中,输入轴经分流机构与液压传动机构传动连接；液压传动机通过构液压分流轴与汇流机构相连；输入轴与机械分流轴同轴固连后,与汇流机构相连；定轴齿轮传动机构分布安装在平行设置的第一中间轴和第二中间轴上,实现多档正反双向传动；汇流机构通过定轴齿轮传动机构与输出轴相连。本发明采用液压、机械功率分流传动技术,将发动机动力分成两路进行传动,一路通过机械回路进行传递,另一路通过液压回路进行传递,最终通过汇流机构将功率汇流输出,结构简单,可实现区段内无级变速,提高传动效率。(The invention discloses a hydraulic mechanical shunt transmission device of a loader, wherein an input shaft is in transmission connection with a hydraulic transmission mechanism through a shunt mechanism; the hydraulic transmission mechanism is connected with the confluence mechanism through a mechanism hydraulic shunt shaft; the input shaft is coaxially and fixedly connected with the mechanical shunt shaft and then connected with the confluence mechanism; the fixed shaft gear transmission mechanisms are distributed and arranged on a first intermediate shaft and a second intermediate shaft which are arranged in parallel, so that multi-gear forward and backward bidirectional transmission is realized; the confluence mechanism is connected with the output shaft through a fixed shaft gear transmission mechanism. The invention adopts hydraulic and mechanical power split transmission technology to divide the power of the engine into two paths for transmission, one path is transmitted through the mechanical circuit, the other path is transmitted through the hydraulic circuit, and finally the power is converged and output through the converging mechanism.)

1. The utility model provides a loader hydromechanical reposition of redundant personnel transmission which characterized in that:

the method comprises the following steps: the device comprises a box body (2), an input shaft (1), a shunt mechanism, a hydraulic transmission mechanism, a confluence mechanism, a hydraulic shunt shaft (45), a mechanical shunt shaft (46), a first intermediate shaft (28), a second intermediate shaft (33), a fixed-shaft gear transmission mechanism and an output shaft (36);

the input shaft (1) is in transmission connection with the hydraulic transmission mechanism through the shunt mechanism;

the hydraulic transmission mechanism is connected with the confluence mechanism through a hydraulic shunt shaft (45);

the input shaft (1) is coaxially and fixedly connected with the mechanical shunt shaft (46) and then is connected with the confluence mechanism;

the fixed-axis gear transmission mechanisms are distributed and arranged on a first intermediate shaft (28) and a second intermediate shaft (33) which are arranged in parallel, so that multi-gear forward and reverse bidirectional transmission is realized;

the confluence mechanism is connected with an output shaft (36) through a fixed shaft gear transmission mechanism.

2. The hydraulic-mechanical split-flow transmission device of the loader as claimed in claim 1, wherein:

the reposition of redundant personnel mechanism includes: third gear (3), tenth gear (10) and k₁A clutch (11);

the third gear (3) is coaxially fixed on the input shaft (1), the tenth gear (10) is meshed with the third gear (3), and k is₁The clutch (11) is arranged and installed between the tenth gear (10) and the mechanical power input end of the hydraulic transmission assembly.

3. The hydraulic-mechanical split-flow transmission device of the loader as claimed in claim 1, wherein:

the hydraulic transmission mechanism includes: a hydraulic variable pump input shaft (7), a hydraulic variable pump (12), a connecting pipeline (13), a hydraulic constant displacement motor (14), a hydraulic constant displacement motor output shaft (15), a sixteenth gear (16) and a k₂A clutch (17) and a twenty-third gear (23);

the input shaft (7) of the hydraulic variable pump is connected with the mechanical power input end of the hydraulic variable pump (12);

the oil port of the hydraulic variable pump (12) is connected with the oil port of the hydraulic constant motor (14) through a connecting pipeline (13);

the output shaft (15) of the hydraulic quantitative motor is connected with the mechanical power output end of the hydraulic quantitative motor (14);

k is₂The clutch (17) is arranged and installed between the sixteenth gear (16) and the output shaft (15) of the hydraulic constant-displacement motor;

the sixteenth gear (16) is in meshed connection with the twenty-third gear (23);

and the twenty-third gear (23) is coaxially fixed on the hydraulic shunt shaft (45).

4. The hydraulic-mechanical split-flow transmission device of the loader as claimed in claim 1, wherein:

the confluence mechanism comprises two groups of planetary gear transmission systems;

in a first planetary gear transmission system, a first sun gear (5) is coaxially fixed on a mechanical shunt shaft (46), a first planetary gear set (8) is fixedly arranged on a first planet carrier (6), the first planetary gear set (8) is respectively meshed with the first sun gear (5) and a first gear ring (9), and the first planet carrier (6) is coaxially and movably sleeved on the mechanical shunt shaft (46);

in the second planetary gear transmission system, a second sun gear (21) is coaxially fixed on a mechanical shunt shaft (46), a second planetary gear set (19) is fixed on a second planet carrier (20), the second planetary gear set (19) is respectively meshed with the second sun gear (21) and a second gear ring (18), one end of the second planet carrier (20) is coaxially fixedly connected with a hydraulic shunt shaft (45), the other end of the second planet carrier (20) is coaxially fixedly connected with a first gear ring (9), and the second gear ring (18) is coaxially movably sleeved on the hydraulic shunt shaft (45).

5. The hydraulic-mechanical split-flow transmission device of the loader as claimed in claim 1, wherein:

in the dead axle gear transmission mechanism:

the fourth gear (4) is coaxially and movably sleeved on the mechanical shunt shaft (46) and is fixedly connected with the first planet carrier (6);

the first intermediate shaft (28) is sequentially provided with: a forty-fourth gear (44) and k which are rotatably arranged and are meshed with the fourth gear (4)₃A clutch (43), a forty-first gear (41) and a k which are rotatably arranged₄A clutch (24), a twenty-fifth gear (25) and a gear k which are arranged in a rotating manner₅A clutch (27) and a rotationally disposed twenty-sixth gear (26);

the twenty-sixth gear (26) is connected with a second twelve gear (22), and the second twelve gear (22) is coaxially and movably sleeved on the hydraulic shunt shaft (45) and is fixedly connected with the second gear ring (18);

the second intermediate shaft (33) is sequentially provided with: a third eighteen gear (38) and a k which are rotatably arranged and are in transmission connection with the fourth gear (4)₆Clutch (39)) A fortieth gear (40) and a k which are arranged in a rotating way₇The clutch (30), a rotationally arranged thirty-first gear (31), a rotationally arranged thirty-fifth gear (35) and a fixedly arranged thirty-fourth gear (34);

the thirty-fifth gear (35) is meshed with a twenty-ninth gear (29), and the twenty-ninth gear (29) is meshed with a twenty-fifth gear (25);

the thirty-fourth gear (34) is coaxially fixed on the second intermediate shaft (33);

a thirty-seventh gear (37) is fixed on the output shaft (36), and the thirty-seventh gear (37) is meshed with the thirty-fourth gear (34).

6. The hydraulic-mechanical shunt transmission device of a loader according to claim 5, wherein:

the fourth gear (4) is directly meshed with the third eighteen gears (38).

7. The hydraulic-mechanical shunt transmission device of a loader according to claim 5, wherein:

the third eighteen gear (38) is in meshed connection with the fourth forty-fourth gear (44), so that the transmission connection with the fourth gear (4) is realized.

8. The hydraulic-mechanical shunt transmission device of a loader according to claim 5, wherein:

the thirty-fifth gear (35) is directly and coaxially connected to the second intermediate shaft (33).

9. The hydraulic-mechanical shunt transmission device of a loader according to claim 5, wherein:

the thirty-fifth gear (35) and the second intermediate shaft (33) pass through k₈The clutch (32) is in transmission connection.

Technical Field

The invention belongs to the technical field of loader transmission devices, and relates to a shunting transmission device, in particular to a hydraulic mechanical shunting transmission device of a loader.

Background

The load of the high-power loader changes frequently, and the operating environment is severe, so that higher requirements are put forward on the variable-speed transmission system. At present, most of the hydromechanical power shift transmissions are used, but the torque converter has problems of narrow high-efficiency range, low transmission efficiency, and the like, and therefore, it has been proposed to improve the transmission efficiency by using a lockup clutch for the torque converter.

The hydrostatic transmission system utilizes the characteristic of volume speed regulation, and can adjust the movement speed of an actuating element by changing the displacement of a variable pump and a variable motor in a loop, so that the loader can finish automatic speed change; however, the hydrostatic transmission adopts a pump-motor closed speed regulation loop, so that the transmission efficiency is lower, and compared with a hydraulic mechanical gearbox, the lifting space is limited.

Disclosure of Invention

Aiming at the defects in the prior art, the invention discloses a hydraulic mechanical shunt transmission device of a loader, which adopts the hydraulic and mechanical power shunt transmission technology to divide the power of an engine into two paths for transmission, wherein one path is transmitted through a mechanical loop, the other path is transmitted through a hydraulic loop, and finally the power is converged and output through a convergence mechanism.

The technical scheme of the invention is as follows by combining the attached drawings of the specification:

a loader hydro-mechanical shunt drive comprising: the device comprises a box body 2, an input shaft 1, a shunting mechanism, a hydraulic transmission mechanism, a confluence mechanism, a hydraulic shunting shaft 45, a mechanical shunting shaft 46, a first intermediate shaft 28, a second intermediate shaft 33, a fixed-shaft gear transmission mechanism and an output shaft 36;

the input shaft 1 is in transmission connection with a hydraulic transmission mechanism through a shunt mechanism;

the hydraulic transmission mechanism is connected with the confluence mechanism through a hydraulic shunting shaft 45;

the input shaft 1 is coaxially and fixedly connected with the mechanical shunt shaft 46 and then connected with the confluence mechanism;

the fixed-axis gear transmission mechanisms are distributed and arranged on a first intermediate shaft 28 and a second intermediate shaft 33 which are arranged in parallel, so that multi-gear forward and backward bidirectional transmission is realized;

the confluence mechanism is connected with an output shaft 36 through a fixed shaft gear transmission mechanism.

Further, the shunt mechanism includes: the third gear 3, the tenth gear 10, and the k1 clutch 11;

the third gear 3 is coaxially fixed on the input shaft 1, the tenth gear 10 is in meshed connection with the third gear 3, and the k1 clutch 11 is arranged and installed between the tenth gear 10 and the mechanical power input end of the hydraulic transmission assembly.

Further, the hydraulic transmission mechanism includes: the hydraulic variable pump comprises a hydraulic variable pump input shaft 7, a hydraulic variable pump 12, a connecting pipeline 13, a hydraulic constant displacement motor 14, a hydraulic constant displacement motor output shaft 15, a sixteenth gear 16, a k2 clutch 17 and a twenty third gear 23;

the input shaft 7 of the hydraulic variable pump is connected with the mechanical power input end of the hydraulic variable pump 12;

the oil port of the hydraulic variable pump 12 is connected with the oil port of the hydraulic constant motor 14 through a connecting pipeline 13;

the output shaft 15 of the hydraulic quantitative motor is connected with the mechanical power output end of the hydraulic quantitative motor 14;

the k2 clutch 17 is arranged and installed between the sixteenth gear 16 and the output shaft 15 of the hydraulic constant displacement motor;

the sixteenth gear 16 is in meshed connection with the twenty-third gear 23;

the twenty-third gear 23 is coaxially fixed to the hydraulic shunt shaft 45.

Further, the confluence mechanism comprises two groups of planetary gear trains;

in the first planetary gear transmission system, a first sun gear 5 is coaxially fixed on a mechanical shunt shaft 46, a first planetary gear set 8 is fixedly arranged on a first planet carrier 6, the first planetary gear set 8 is respectively meshed with the first sun gear 5 and a first gear ring 9, and the first planet carrier 6 is coaxially and movably sleeved on the mechanical shunt shaft 46;

in the second planetary gear transmission system, the second sun gear 21 is coaxially fixed on the mechanical shunt shaft 46, the second planetary gear set 19 is fixed on the second planet carrier 20, the second planetary gear set 19 is respectively meshed with the second sun gear 21 and the second gear ring 18, one end of the second planet carrier 20 is coaxially fixedly connected with the hydraulic shunt shaft 45, the other end of the second planet carrier 20 is coaxially fixedly connected with the first gear ring 9, and the second gear ring 18 is coaxially movably sleeved on the hydraulic shunt shaft 45.

Further, in the fixed-axis gear transmission mechanism:

the fourth gear 4 is coaxially and movably sleeved on the mechanical shunt shaft 46 and is fixedly connected with the first planet carrier 6;

the first intermediate shaft 28 is sequentially provided with: a forty-fourth gear 44 k rotatably disposed and engaged with the fourth gear 4₃Clutch 43, and forty-first gear 41, k provided rotatably₄Clutch 24, a rotationally disposed twenty-fifth gear 25, k₅A clutch 27 and a rotationally disposed twenty-sixth gear 26;

the twenty-sixth gear 26 is connected with the second twenty-gear 22, and the second twelfth gear 22 is coaxially and movably sleeved on the hydraulic shunt shaft 45 and is fixedly connected with the second gear ring 18;

the second intermediate shaft 33 is sequentially provided with: a third eighteen gear 38, k which is rotatably arranged and is in transmission connection with the fourth gear 4₆Clutch 39, and a forty-gear 40, k rotatably provided₇A clutch 30, a rotationally disposed thirty-first gear 31, a rotationally disposed thirty-fifth gear 35 and a fixedly disposed thirty-fourth gear 34;

the thirty-fifth gear 35 is meshed with the twenty-ninth gear 29, and the twenty-ninth gear 29 is meshed with the twenty-fifth gear 25;

the thirty-fourth gear 34 is coaxially fixed on the second intermediate shaft 33;

a thirty-seventh gear 37 is fixed to the output shaft 36, and the thirty-seventh gear 37 meshes with the thirty-fourth gear 34.

Further, the fourth gear 4 is in direct meshed connection with the thirty-eighth gear 38.

Further, the eighteenth gear 38 is in meshed connection with the forty-fourth gear 44, so as to realize transmission connection with the fourth gear 4.

Further, the thirty-fifth gear 35 is directly coaxially attached to the second countershaft 33.

Further, the thirty-fifth gear 35 and the second intermediate shaft 33 pass through k₈The clutch 32 is drivingly connected.

Compared with the prior art, the invention has the beneficial effects that:

1. the hydraulic mechanical shunt transmission device of the loader divides the power of the engine into two paths for transmission, one path is transmitted through the mechanical path, the other path is transmitted through the hydraulic road roller, and finally the power is converged and output through the convergence mechanism, so that high-efficiency transmission and continuous stepless adjustment of the transmission ratio can be realized.

2. The hydraulic mechanical shunt transmission device of the loader adopts a hydraulic mechanical continuous transmission mode, removes a pure hydraulic transmission mode, and improves transmission efficiency compared with a traditional hydraulic mechanical power shift gearbox and hydrostatic transmission.

3. The hydraulic mechanical shunt transmission device of the loader can meet the complex working requirements. Mechanical gears can be used to meet the requirements of use if necessary.

4. The hydraulic mechanical shunt transmission device of the loader can be used for firstly engaging the next section of clutch and releasing the previous section of clutch, so that the output of power is not interrupted in the adjusting process, and the working efficiency is improved.

5. The hydraulic mechanical shunt transmission device of the loader can realize continuous stepless adjustment of the transmission ratio, does not interrupt power transmission in the adjustment process, has high transmission efficiency, can ensure that an engine works under the condition of highest efficiency, and improves the fuel economy.

Drawings

FIG. 1 is a schematic transmission diagram of a hydraulic mechanical shunt transmission of a loader according to an embodiment of the invention;

FIG. 2 is a diagram of an engaged state of a transmission shift element in accordance with one embodiment of the present invention;

FIG. 3 is a schematic diagram of the power flow of the forward hydraulic machine 1 speed in accordance with one embodiment of the present invention;

FIG. 4 is a schematic diagram of the forward 2 speed power flow of the hydraulic machine of the transmission according to the first embodiment of the present invention;

FIG. 5 is a schematic diagram of the forward 3 speed power flow of the hydraulic machine of the transmission according to the first embodiment of the present invention;

FIG. 6 is a schematic diagram of the forward mechanical 1-speed power flow of the transmission according to one embodiment of the present invention;

FIG. 7 is a schematic diagram of the forward mechanical 2 speed power flow of the transmission according to one embodiment of the present invention;

FIG. 8 is a schematic illustration of the forward mechanical 3 speed power flow of the transmission according to one embodiment of the present invention;

FIG. 9 is a schematic diagram of the reverse hydromechanical 1-speed power flow of the transmission according to one embodiment of the present invention;

FIG. 10 is a schematic diagram of the reverse 2 speed power flow of the transmission according to one embodiment of the present invention;

FIG. 11 is a schematic diagram of the reverse 3-speed power flow of the transmission according to one embodiment of the present invention;

FIG. 12 is a schematic diagram of reverse mechanical 1 speed power flow of the transmission according to one embodiment of the present invention;

FIG. 13 is a schematic diagram of the reverse mechanical 2 speed power flow of the transmission according to one embodiment of the present invention;

FIG. 14 is a schematic illustration of the reverse mechanical 3 speed power flow of the transmission according to one embodiment of the present invention;

FIG. 15 is a simplified drive diagram of a hydraulic-mechanical split-flow drive of a loader according to an embodiment of the present invention;

fig. 16 is a schematic transmission diagram of a hydraulic mechanical shunt transmission of the loader according to the first embodiment of the invention.

In the figure:

1 input shaft, 2 boxes, 3 third gears,

4 fourth gear, 5 first sun gear, 6 first planet carrier,

7 hydraulic variable pump input shaft, 8 first planetary gear set, 9 first gear ring,

10 tenth gear, 11k₁A clutch, a 12 hydraulic variable pump,

13 connecting pipelines, 14 hydraulic quantitative motors, 15 hydraulic quantitative motor output shafts,

16 sixteenth gear, 17k₂A clutch, 18 second gear rings,

19 second planetary gear set, 20 second planetary gear carrier, 21 second sun gear,

22 second twelve gears, 23 twenty third gears, 24k₄A clutch,

25 twenty-fifth gear, 26 twenty-sixth gear, 27k₅A clutch,

28 first countershaft, 29 twenty-ninth gear, 30k₇A clutch,

31 thirty-first gear, 32k₈A clutch 33, a second intermediate shaft,

34 a thirty-fourth gear, 35 a thirty-fifth gear, 36 an output shaft,

37 thirty-seventh gear, 38 thirty-eighth gear, 39k₆A clutch,

40 fourth gear, 41 fourth gear, 42 fourth twelve gear,

43k₃A clutch, a 44 th forty-fourth gear, a 45 hydraulic shunt shaft,

46 mechanical diverter shaft.

Detailed Description

For clearly and completely describing the technical scheme and the specific working process thereof, the specific implementation mode of the invention is as follows by combining the attached drawings of the specification:

in the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

The first embodiment is as follows:

as shown in fig. 1, the first embodiment discloses a hydraulic mechanical split transmission device of a loader, which includes a box 2, an input shaft 1, a split mechanism, a hydraulic transmission mechanism, a confluence mechanism, a hydraulic split shaft 45, a mechanical split shaft 46, a first intermediate shaft 28, a second intermediate shaft 33, a fixed-axis gear transmission mechanism, and an output shaft 36.

The input shaft 1 is used as a power input end of the whole transmission device and penetrates through and is supported and installed on the box body 2.

The reposition of redundant personnel mechanism includes: third gear 3, tenth gear 10 and k₁A clutch 11; wherein, the firstThe third gear 3 is coaxially fixed on the input shaft 1, the tenth gear 10 is meshed with the third gear 3, and k is₁A clutch 11 is provided between the tenth gear 10 and the input shaft 7 of the hydraulic variable displacement pump in the hydraulic transmission assembly, where k₁The driving member of the clutch 11 is fixed to the tenth gear 10, k₁The driven part of the clutch 11 is fixed on the input shaft 7 of the hydraulic variable pump, and k is₁The clutch 11 controls the engagement or disengagement of the tenth gear 10 with or from the hydraulic variable pump input shaft 7 to achieve the transmission or disconnection of power.

The hydraulic transmission mechanism includes: a hydraulic variable pump input shaft 7, a hydraulic variable pump 12, a connecting pipeline 13, a hydraulic constant displacement motor 14, a hydraulic constant displacement motor output shaft 15, a sixteenth gear 16, k₂The clutch 17 and the twenty-third gear 23; the input shaft 7 of the hydraulic variable pump is connected with the mechanical power input end of the hydraulic variable pump 12, and an oil port of the hydraulic variable pump 12 is connected with an oil port of the hydraulic constant-displacement motor 14 through a connecting pipeline 13; the output shaft 15 of the hydraulic quantitative motor is connected with the mechanical power output end of the hydraulic quantitative motor 14, and the output shaft 15 of the hydraulic quantitative motor is supported and installed on the box body 2; k is₂A clutch 17 is provided between the sixteenth gear 16 and the hydraulic constant displacement motor output shaft 15, wherein k₂The driving part of the clutch 17 is fixed on the output shaft 15 of the hydraulic constant-displacement motor, k₂The driven member of the clutch 17 is fixed to the sixteenth gear 16, k₂The clutch 17 controls the combination or separation of the sixteenth gear 16 and the output shaft 15 of the hydraulic constant displacement motor to realize the transmission or disconnection of power, the sixteenth gear 16 is in meshed connection with a twenty-third gear 23, and the twenty-third gear 23 is coaxially fixed on the hydraulic shunt shaft 45.

The hydraulic shunt shaft 45 is supported and mounted on the box body 2.

The mechanical shunt shaft 46 is coaxially arranged with the input shaft 1 and is of an integrated structure with the input shaft 1.

The confluence mechanism includes: a first planetary gear train consisting of the first sun gear 5, the first planet carrier 6, the first planetary gear set 8 and the first ring gear 9, and a second planetary gear train consisting of the second sun gear 21, the second planet carrier 20, the second planetary gear set 19 and the second ring gear 18;

in the first planetary gear transmission system, a first sun gear 5 is coaxially fixed on a mechanical shunt shaft 46, a first planetary gear set 8 is fixedly arranged on a first planet carrier 6, the inner side of the revolution circumference of the first planetary gear set 8 is meshed with the first sun gear 5, the outer side of the revolution circumference of the first planetary gear set 8 is meshed with a first gear ring 9, and the first planet carrier 6 is coaxially and movably sleeved on the mechanical shunt shaft 46;

in the second planetary gear transmission system, the second sun gear 21 is coaxially fixed on the mechanical shunt shaft 46, the second planetary gear set 19 is fixed on the second planet carrier 20, the inner side of the revolution circumference of the second planetary gear set 19 is meshed with the second sun gear 21, the outer side of the revolution circumference of the second planetary gear set 19 is meshed with the second gear ring 18, one end of the second planet carrier 20 is coaxially and fixedly connected with the hydraulic shunt shaft 45, the other end of the second planet carrier 20 is coaxially and fixedly connected with the first gear ring 9, and the second gear ring 18 is coaxially and movably sleeved on the hydraulic shunt shaft 45.

The dead axle gear transmission mechanism includes: positive dead axle gear drive group and reverse dead axle gear drive group, wherein, positive dead axle gear drive group includes: the device comprises a forward section I fixed-axis gear transmission assembly, a forward section II fixed-axis gear transmission assembly and a forward section III fixed-axis gear transmission assembly; the reverse dead axle gear transmission set comprises: the reverse I section fixed shaft gear transmission component, the reverse II section fixed shaft gear transmission component and the reverse III section fixed shaft gear transmission component;

the I section dead axle gear drive assembly in forward includes: fourth gear 4, forty-fourth gear 44, k₃Clutch 43, forty-first gear 41, forty-second gear 40, k₇The clutch 30, the thirty-first gear 31, the thirty-fourth gear 34, and the thirty-seventh gear 37; wherein:

the fourth gear 4 is coaxially and movably sleeved on a mechanical diverter shaft 46 and is fixedly connected with the first planet carrier 6, the fourth gear 4 is meshed with a forty-fourth gear 44, and the forty-fourth gear 44 is coaxially and movably sleeved on the first intermediate shaft 28; the first isThe intermediate shaft 28 penetrates through the box body 2, and two ends of the first intermediate shaft 28 are respectively supported and installed on the box body 2; the forty-first gear 41 is coaxially and movably sleeved on the first intermediate shaft 28; k is₃The clutch 43 is arranged between the forty-fourth gear 44 and the forty-first gear 41, wherein k₃The driving member of the clutch 43 is fixed to the forty-fourth gear 44, k₃The passive member of the clutch 43 is fixed to the forty-first gear 41, k₃The clutch 43 controls the connection or disconnection of the forty-fourth gear 44 and the forty-first gear 41 to realize the transmission or disconnection of power; the forty-first gear 40 is coaxially and movably sleeved on the second intermediate shaft 33 and is meshed with the forty-first gear 41; the second intermediate shaft 33 penetrates through the box body 2, and two ends of the second intermediate shaft 33 are respectively supported and installed on the box body 2; the thirty-first gear 31 is coaxially fixed on the second intermediate shaft 33; k is₇The clutch 30 is arranged and installed between the fortieth gear 40 and the thirty-first gear 31, wherein k is₇The driving member of the clutch 30 is fixed to the fortieth gear 40, k₇The driven member of the clutch 30 is fixed to the thirty-first gear 31; the thirty-fourth gear 34 is coaxially fixed on the second intermediate shaft 33; the thirty-seventh gear 37 is coaxially fixed on the output shaft 36; the thirty-fourth gear 34 meshes with a thirty-seventh gear 37.

The forward II-section dead axle gear transmission assembly comprises: the twenty-second gear 22, the twenty-sixth gear 26, k₅Clutch 27, twenty-fifth gear 25, k₄Clutch 24, forty-first gear 41, forty-second gear 40, k₇The clutch 30, the thirty-first gear 31, the thirty-fourth gear 34, and the thirty-seventh gear 37;

the second gear 22 is coaxially and movably sleeved on the hydraulic shunt shaft 45 and is fixedly connected with the second gear ring 18, the second gear 22 is meshed with a twenty-sixth gear 26, and the twenty-sixth gear 26 is coaxially and movably sleeved on the first intermediate shaft 28; the twenty-fifth gear 25 is coaxially and movably sleeved on the first intermediate shaft 28; k is₅A clutch 27 is arranged between the twenty-sixth gear 26 and the twenty-fifth gear 25Wherein k is₅The driving member of the clutch 27 is fixed to the twenty-sixth gear 26, k₅The driven member of the clutch 27 is fixed to the twenty-fifth gear 25; k is₄The clutch 24 is arranged and mounted between the twenty-fifth gear 25 and the forty-first gear 41, wherein k₄The driving member of the clutch 24 is fixed to the twenty-fifth gear 25, k₄The driven member of the clutch 24 is fixed to the forty-first gear 41, k₄The clutch 24 controls the connection or disconnection of the twenty-fifth gear 25 and the forty-first gear 41 to realize the transmission or disconnection of power; the forty-first gear 41, the forty-second gear 40, k₇The mounting and connecting structures of the clutch 30, the thirty-first gear 31, the thirty-fourth gear 34 and the thirty-seventh gear 37 are as described above, and will not be described herein.

The forward III-section dead axle gear transmission comprises: fourth gear 4, thirty-eighth gear 38, k₆Clutch 39, fortieth gear 40, k₇The clutch 30, the thirty-first gear 31, the thirty-fourth gear 34, and the thirty-seventh gear 37;

the fourth gear 4 is coaxially and movably sleeved on the mechanical shunt shaft 46 and is fixedly connected with the first planet carrier 6; the thirty-eighth gear 38 is coaxially and movably sleeved on the second intermediate shaft 33 and is meshed with the fourth gear 4; k is₆The clutch 39 is disposed between the thirty-eighth gear 38 and the fortieth gear 40, wherein k₆The driving member of the clutch 39 is fixed to the thirty-eighth gear 38, k₆The driven member of the clutch 39 is fixed to a fortieth gear 40, k₆The clutch 39 controls the connection or disconnection of the thirty-eighth gear 38 and the fortieth gear 40 to realize the transmission or disconnection of power; the fortieth gear 40, k₇The mounting and connecting structures of the clutch 30, the thirty-first gear 31, the thirty-fourth gear 34 and the thirty-seventh gear 37 are as described above, and are not described herein again.

The I section dead axle gear drive of reverse includes: fourth gear 4, forty-fourth gear 44, k₃Clutch 43 and forty-first gear 41, k₄Clutch 24, twenty-fifth gear 25, twenty-ninth gear 29, thirty-fifth gearWheels 35, k₈The clutch 32, the thirty-first gear 31, the thirty-fourth gear 34, and the thirty-seventh gear 37;

the fourth gear 4 is coaxially and movably sleeved on the mechanical shunt shaft 46 and is fixedly connected with the first planet carrier 6; the 44 th gear 44 is coaxially and movably sleeved on the first intermediate shaft 28, and the fourth gear 4 is meshed with the forty-fourth gear 44; the forty-first gear 41 is coaxially and movably sleeved on the first intermediate shaft 28; k is₃The clutch 43 is arranged between the forty-fourth gear 44 and the forty-first gear 41, wherein k₃The driving member of the clutch 43 is fixed to the forty-fourth gear 44, k₃The passive member of the clutch 43 is fixed to the forty-first gear 41, k₃The clutch 43 controls the connection or disconnection of the forty-fourth gear 44 and the forty-first gear 41 to realize the transmission or disconnection of power; the twenty-fifth gear 25 is coaxially and movably sleeved on the first intermediate shaft 28; k is₄The clutch 24 is arranged and mounted between the twenty-fifth gear 25 and the forty-first gear 41, wherein k₄The driving member of the clutch 24 is fixed to the twenty-fifth gear 25, k₄The driven member of the clutch 24 is fixed to the forty-first gear 41, k₄The clutch 24 controls the connection or disconnection of the twenty-fifth gear 25 and the forty-first gear 41 to realize the transmission or disconnection of power; the twenty-ninth gear 29 is meshed with the twenty-fifth gear 25 and the thirty-fifth gear 35 respectively; the thirty-fifth gear 35 is coaxially arranged with the second intermediate shaft 33, and k is₈The clutch 32 is arranged between the thirty-fifth gear 35 and the second countershaft 33, wherein k₈The driving member of the clutch 32 is fixedly connected with a thirty-fifth gear 35, k₈The driven part of the clutch 32 is fixedly connected with the second intermediate shaft 33; the thirty-fourth gear 34 is coaxially fixed to the second intermediate shaft 33, and the thirty-fourth gear 34 meshes with a thirty-seventh gear 37 coaxially fixed to the output shaft 36.

The reverse II-section dead axle gear transmission comprises: the twenty-second gear 22, the twenty-sixth gear 26, k₅A clutch 27, a twenty-fifth gear 25, a twenty-ninth gear 29, a thirty-fifth gear 35,k₈The clutch 32, the thirty-first gear 31, the thirty-fourth gear 34, and the thirty-seventh gear 37;

the second gear 22 is coaxially and movably sleeved on the hydraulic shunt shaft 45 and is fixedly connected with the second gear ring 18, the second gear 22 is meshed with a twenty-sixth gear 26, and the twenty-sixth gear 26 is coaxially and movably sleeved on the first intermediate shaft 28; the twenty-fifth gear 25 is coaxially and movably sleeved on the first intermediate shaft 28; k is₅A clutch 27 is arranged between the twenty-sixth gear 26 and the twenty-fifth gear 25, where k₅The driving member of the clutch 27 is fixed to the twenty-sixth gear 26, k₅The driven member of the clutch 27 is fixed to the twenty-fifth gear 25; the twenty-fifth gear 25, the twenty-ninth gear 29, the thirty-fifth gear 35, k₈The mounting and connecting structures of the clutch 32, the thirty-first gear 31, the thirty-fourth gear 34 and the thirty-seventh gear 37 are as described above, and will not be described herein again.

The reverse III-section dead axle gear transmission comprises: fourth gear 4, thirty-eighth gear 38, k₆Clutch 39, forty-first gear 40, forty-first gear 41, k₄Clutch 24, twenty-fifth gear 25, twenty-ninth gear 29, thirty-fifth gear 35, k₈The clutch 32, the thirty-first gear 31, the thirty-fourth gear 34, and the thirty-seventh gear 37;

the fourth gear 4 is coaxially and movably sleeved on the mechanical shunt shaft 46 and is fixedly connected with the first planet carrier 6; the thirty-eighth gear 38 is coaxially and movably sleeved on the second intermediate shaft 33 and is meshed with the fourth gear 4; the forty-first gear 40 is coaxially and movably sleeved on the second intermediate shaft 33 and is meshed with the forty-first gear 41; the forty-first gear 41 is coaxially and movably sleeved on the first intermediate shaft 28; k is₆The clutch 39 is disposed between the thirty-eighth gear 38 and the fortieth gear 40, wherein k₆The driving member of the clutch 39 is fixed to the thirty-eighth gear 38, k₆The driven member of the clutch 39 is fixed to a fortieth gear 40, k₆With clutch 39 controlling thirty-eighth gear 38 and fortieth gear 40Combining or separating to realize power transmission or disconnection; k is₄The clutch 24 is arranged and mounted between the twenty-fifth gear 25 and the forty-first gear 41, wherein k₄The driving member of the clutch 24 is fixed to the twenty-fifth gear 25, k₄The driven member of the clutch 24 is fixed to the forty-first gear 41, k₄The clutch 24 controls the connection or disconnection of the twenty-fifth gear 25 and the forty-first gear 41 to realize the transmission or disconnection of power; the twenty-fifth gear 25, the twenty-ninth gear 29, the thirty-fifth gear 35, k₈The mounting and connecting structures of the clutch 32, the thirty-first gear 31, the thirty-fourth gear 34 and the thirty-seventh gear 37 are as described above, and will not be described herein again.

In the above-mentioned dead axle gear drive, the shaft section that takes place separately, as shown in fig. 1, the structure is specifically as follows:

the first intermediate shaft 28 is sequentially provided with: a forty-fourth gear 44 k rotatably provided₃Clutch 17, and forty-first gear 41, k rotatably provided₄Clutch 24, a rotationally disposed twenty-fifth gear 25, k₅A clutch 27, a twenty-sixth gear 26 rotatably disposed; wherein: the forty-fourth gear 44 meshes with the fourth gear 4, and the forty-fourth gear 44 meshes with the k₃Clutch 43 drive member connection, k₃The clutch 43 is connected to the forty-first gear 41 as a driven member, and the forty-first gear 41 is connected to the gear k₄Clutch 24 drive member connection, k₄The clutch 24 is connected with the twenty-fifth gear 25 by the driven member, and the twenty-fifth gear 25 is connected with the k₅The driving part of the clutch 27 is connected, k₅The driven piece of the clutch 27 is connected with the twenty-sixth gear 26, the twenty-sixth gear 26 is connected with the second twenty-gear 22, and the second twelfth gear 22 is coaxially and movably sleeved on the hydraulic shunt shaft 45 and is fixedly connected with the second gear ring 18;

the second intermediate shaft 33 is sequentially provided with: thirty-eighth gear 38, k₆Clutch 39, and a forty-gear 40, k rotatably provided₇Clutch 30, rotatably arranged thirty-oneGear 31, k₈A clutch 32, a rotationally disposed thirty-fifth gear 35 and a fixedly disposed thirty-fourth gear 34; wherein: the eighteenth gear 38 is engaged with the fourth gear 4, and the thirty-eighth gear 38 is engaged with the k₆Clutch 39 drive connection, k₆The clutch 39 is connected to the forty-th gear 40 by a driven member, and the forty-th gear 40 is connected to the gear k₇The driving member of the clutch 30 is connected, k₇The clutch 30 driven piece is connected with the thirty-first gear 31; the thirty-fifth gear 35 is meshed with the twenty-ninth gear 29, the twenty-ninth gear 29 is meshed with the twenty-fifth gear 25, and the 35-th gear 35 is meshed with the k₈The driving member of the clutch 32 is connected, k₈The clutch 32 driven part is connected with the second intermediate shaft 33; the thirty-fourth gear 34 is coaxially fixed on the second intermediate shaft 33;

the output shaft 36 is fixedly provided with the thirty-seventh gear 37, and the thirty-seventh gear 37 is meshed with the thirty-fourth gear 34.

In order to provide multi-gear selection, hydraulic mechanical split transmission and mechanical transmission under forward transmission and hydraulic mechanical split transmission and mechanical transmission under reverse transmission are realized through mutual combination switching among clutches; the path transmission of each gear of the hydraulic mechanical shunt transmission device of the loader is as follows by combining the attached drawings of the specification:

as shown in fig. 2 and 3, the forward hydromechanical 1-gear path is transmitted as:

k₁clutch 11, k₂Clutch 17, k₃Clutch 43 and k₇Clutch 30 engaged, k₄Clutch 24, k₅Clutch 27, k₆Clutch 39 and k₈The clutch 32 is disengaged;

on the one hand, the hydraulic path transmits power: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁The clutch 11 is transmitted from the input shaft 7 of the hydraulic variable pump to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 passes through the hydraulic constant rate motor 14 and then is output from the output shaft of the hydraulic constant rate motor15 in turn are passed on to k₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are sequentially transmitted to the second planet carrier 20, the first ring gear 9 and the first planet gear set 8 through a hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the first sun gear 5 and the first planetary gear set 8 through the input shaft 1 and the mechanical shunt shaft 46;

the hydraulic path transmission power and the mechanical path transmission power are combined at the first carrier 6, and the power is transmitted to the gear k through the fourth gear 4 and the forty-fourth gear 44 in this order₃The clutch 43 transmits power to the gear k via the eleventh gear 41 and the fortieth gear 40 in this order₇The clutch 30 finally transmits power to the output shaft 36 via the thirty-first gear 31, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and thereby achieves power output.

As shown in fig. 2 and 4, the forward hydromechanical 2-speed path is transmitted as:

k₁clutch 11, k₂Clutch 17, k₄Clutch 24, k₅Clutch 27 and k₇Clutch 30 engaged, k₃Clutch 43, k₆Clutch 39 and k₈The clutch 32 is disengaged;

on the one hand, the hydraulic path transmits power: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁The clutch 11 is transmitted from the input shaft 7 of the hydraulic variable pump to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 is transmitted to the constant displacement motor 14 and then transmitted to the motor k sequentially from the output shaft 15 of the constant displacement motor₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are transmitted to the second carrier 20 through the hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the second sun gear 21 and the second planetary gear set 19 through the input shaft 1 and the mechanical split shaft 46;

according to the transmission characteristics of the planetary gear train, the second planet carrier 20, the second sun gear 21 and the second planetary gear set 19 drive the second gear ring 18 to move;

the hydraulic path transmission power and the mechanical path transmission power are combined at the second ring gear 18 and transmitted to k through the twenty-second and twenty-sixth gears 22 and 26 in order₅Clutch 27, then to k via twenty-fifth gear 25₄The clutch 24 transmits power to the gear k via the eleventh gear 41 and the fortieth gear 40 in this order₇The clutch 30 finally transmits power to the output shaft 36 via the thirty-first gear 31, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and thereby achieves power output.

As shown in fig. 2 and 5, the forward hydromechanical 3-speed path is:

k₁clutch 11, k₂Clutch 17, k₆Clutch 39 and k₇Clutch 30 engaged, k₃Clutch 43, k₄Clutch 24, k₅Clutch 27 and k₈The clutch 32 is disengaged;

on the one hand, the hydraulic path transmits power: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁The clutch 11 is transmitted from the input shaft 7 of the hydraulic variable pump to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 is transmitted to the constant displacement motor 14 and then transmitted to the motor k sequentially from the output shaft 15 of the constant displacement motor₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are sequentially transmitted to the second planet carrier 20, the first ring gear 9 and the first planet gear set 8 through a hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the first sun gear 5 and the first planetary gear set 8 through the input shaft 1 and the mechanical shunt shaft 46;

the hydraulic path transmission power and the mechanical path transmission power are combined at the first carrier 6 and transmitted to k through the fourth gear 4 and the thirty-eighth gear 38 in this order₆Clutch 39, via a fortieth gear 40, transmits power to k₇The clutch 30 finally transmits power to the output shaft 36 via the thirty-first gear 31, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and thereby achieves power output.

As shown in fig. 2 and 6, the forward mechanical 1 st gear path is:

k₃clutch 43 and k₇Clutch 30 engaged, k₁Clutch 11, k₂Clutch 17, k₄Clutch 24, k₅Clutch 27, k₆Clutch 39 and k₈The clutch 32 is disengaged;

the engine input power is transmitted to the first sun gear 5, the first planetary gear set 8 and the first planet carrier 6 in sequence through the input shaft 1 and the mechanical shunt shaft 46, and then transmitted to the gear k in sequence through the fourth gear 4 and the fourth twelve gear 42₃The clutch 43 transmits power to the gear k via the eleventh gear 41 and the fortieth gear 40 in this order₇The clutch 30 finally transmits power to the output shaft 36 via the thirty-first gear 31, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and thereby achieves power output.

As shown in fig. 2 and 7, the forward machine 2-speed path is:

k₄clutch 24, k₅Clutch 27 and k₇Clutch 30 engaged, k₁Clutch 11, k₂Clutch 17, k₃Clutch 43, k₆Clutch 39 and k₈The clutch 32 is disengaged;

the engine input power is transmitted to the second sun gear 21, the second planetary gear set 19 and the second ring gear 18 through the input shaft 1 and the mechanical split shaft 46, and is transmitted to the gear k through the twenty-second gear 22 and the twenty-sixth gear 26 in sequence₅Clutch 27, then to k via twenty-fifth gear 25₄The clutch 24 transmits power to the gear k via the eleventh gear 41 and the fortieth gear 40 in this order₇The clutch 30 finally transmits power to the output shaft 36 via the thirty-first gear 31, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and thereby achieves power output.

As shown in fig. 2 and 8, the forward mechanical 3-speed path is:

k₆clutch 39 and k₇Clutch 30 engaged, k₁Clutch 11, k₂ClutchDevice 17, k₃Clutch 43, k₄Clutch 24, k₅Clutch 27 and k₈The clutch 32 is disengaged;

the engine input power is transmitted to the first sun gear 5, the first planetary gear set 8 and the first carrier 6 through the input shaft 1 and the mechanical split shaft 46, and then transmitted to the gear k through the fourth gear 4 and the thirty-eighth gear 38 in sequence₆Clutch 39, via a fortieth gear 40, transmits power to k₇The clutch 30 finally transmits power to the output shaft 36 via the thirty-first gear 31, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and thereby achieves power output.

As shown in fig. 2 and 9, the reverse hydro-mechanical 1-gear path is transferred as:

k₁clutch 11, k₂Clutch 17, k₃Clutch 43, k₄Clutch 24 and k₈Clutch 32 engaged, k₅Clutch 27, k₆Clutch 39 and k₇The clutch 30 is disengaged;

on the one hand, the hydraulic path transmits power: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁The clutch 11 is transmitted from the input shaft 7 of the hydraulic variable pump to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 is transmitted to the constant displacement motor 14 and then transmitted to the motor k sequentially from the output shaft 15 of the constant displacement motor₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are sequentially transmitted to the second planet carrier 20, the first ring gear 9 and the first planet gear set 8 through a hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the first sun gear 5 and the first planetary gear set 8 through the input shaft 1 and the mechanical shunt shaft 46;

the hydraulic path transmission power and the mechanical path transmission power are combined at the first carrier 6, and the power is transmitted to the gear k through the fourth gear 4 and the forty-fourth gear 44 in this order₃Clutch 43, which in turn transmits power to k via forty-first gear 41₄Clutch 24, in turn, transmits power through twenty-fifth gear 25, twenty-ninth gear 29, and thirty-fifth gear 35Is transmitted to k₈The clutch 32 finally transmits power to the output shaft 36 via the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and the power output is realized.

As shown in fig. 2 and 10, the reverse hydro-mechanical 2-speed path is transferred as:

k₁clutch 11, k₂Clutch 17, k₅Clutch 27, and k₈Clutch 32 engaged, k₃Clutch 43, k₄Clutch 24, k₆Clutch 39 and k₇The clutch 30 is disengaged;

on the one hand, the hydraulic path transmits power: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁The clutch 11 is transmitted from the input shaft 7 of the hydraulic variable pump to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 is transmitted to the constant displacement motor 14 and then transmitted to the motor k sequentially from the output shaft 15 of the constant displacement motor₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are transmitted to the second carrier 20 through the hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the second sun gear 21 and the second planetary gear set 19 through the input shaft 1 and the mechanical split shaft 46;

according to the transmission characteristics of the planetary gear train, the second planet carrier 20, the second sun gear 21 and the second planetary gear set 19 drive the second gear ring 18 to move;

the hydraulic path transmission power and the mechanical path transmission power are combined at the second ring gear 18 and transmitted to k through the twenty-second and twenty-sixth gears 22 and 26 in order₅The clutch 27, in turn, transmits power to k through the twenty-fifth gear 25, the twenty-ninth gear 29, and the thirty-fifth gear 35 in that order₈The clutch 32 finally transmits power to the output shaft 36 via the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and the power output is realized.

As shown in fig. 2 and 11, the reverse hydro-mechanical 3-speed path is transferred as:

k₁clutch 11, k₂A clutch 17,k₄Clutch 24, k₆Clutch 39 and k₈Clutch 32 engaged, k₃Clutch 43, k₅Clutch 27 and k₇The clutch 30 is disengaged;

on the one hand, the hydraulic path transmits power: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁The clutch 11 is transmitted from the input shaft 7 of the hydraulic variable pump to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 is transmitted to the constant displacement motor 14 and then transmitted to the motor k sequentially from the output shaft 15 of the constant displacement motor₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are sequentially transmitted to the second planet carrier 20, the first ring gear 9 and the first planet gear set 8 through a hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the first sun gear 5 and the first planetary gear set 8 through the input shaft 1 and the mechanical shunt shaft 46;

the hydraulic path transmission power and the mechanical path transmission power are combined at the first carrier 6 and transmitted to k through the fourth gear 4 and the thirty-eighth gear 38 in this order₆The clutch 39 transmits power to the gear k via a fortieth gear 40 and a fortieth gear 41 in this order₄The clutch 24, in turn, transmits power to k through the twenty-fifth gear 25, the twenty-ninth gear 29, and the thirty-fifth gear 35 in that order₈The clutch 32 finally transmits power to the output shaft 36 via the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and the power output is realized.

As shown in fig. 2 and 12, the reverse mechanical 1-gear path is:

k₃clutch 43, k₄Clutch 24 and k₈Clutch 32 engaged, k₁Clutch 11, k₂Clutch 17, k₅Clutch 27, k₆Clutch 39 and k₇The clutch 30 is disengaged;

the engine input power is transmitted to the first sun gear 5, the first planetary gear set 8 and the first planet carrier 6 in sequence through the input shaft 1 and the mechanical shunt shaft 46, and then transmitted to the gear k in sequence through the fourth gear 4 and the fourth twelve gear 42₃Clutch 43 for transmitting power to k through the fourth eleventh gear 41₄The clutch 24, in turn, transmits power to k through the twenty-fifth gear 25, the twenty-ninth gear 29, and the thirty-fifth gear 35 in that order₈The clutch 32 finally transmits power to the output shaft 36 via the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and the power output is realized.

As shown in fig. 2 and 13, the reverse machine 2-gear path is:

k₅clutch 27 and k₈Clutch 32 engaged, k₁Clutch 11, k₂Clutch 17, k₃Clutch 43, k₄Clutch 24, k₆Clutch 39 and k₇The clutch 30 is disengaged;

the engine input power is transmitted to the second sun gear 21, the second planetary gear set 19 and the second ring gear 18 through the input shaft 1 and the mechanical split shaft 46, and is transmitted to the gear k through the twenty-second gear 22 and the twenty-sixth gear 26 in sequence₅The clutch 27, in turn, transmits power to k through the twenty-fifth gear 25, the twenty-ninth gear 29, and the thirty-fifth gear 35 in that order₈The clutch 32 finally transmits power to the output shaft 36 via the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and the power output is realized.

As shown in fig. 2 and 14, the reverse mechanical 3-gear path is:

k₄clutch 24, k₆Clutch 39 and k₈Clutch 32 engaged, k₁Clutch 11, k₂Clutch 17, k₃Clutch 43, k₅Clutch 27 and k₇The clutch 30 is disengaged;

the engine input power is transmitted to the first sun gear 5, the first planetary gear set 8 and the first carrier 6 through the input shaft 1 and the mechanical split shaft 46, and then transmitted to the gear k through the fourth gear 4 and the thirty-eighth gear 38 in sequence₆The clutch 39 transmits power to the gear k via a fortieth gear 40 and a fortieth gear 41 in this order₄The clutch 24, in turn, transfers power through a twenty-fifth gear 25, a twenty-ninth gear 29, and a thirty-fifth gear 35 in that orderDelivered to k₈The clutch 32 finally transmits power to the output shaft 36 via the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and the power output is realized.

Example two:

as shown in fig. 15, the second embodiment discloses a hydraulic mechanical split transmission device of a loader, which includes a box 2, an input shaft 1, a split mechanism, a hydraulic transmission mechanism, a confluence mechanism, a hydraulic split shaft 45, a mechanical split shaft 46, a first intermediate shaft 28, a second intermediate shaft 33, a fixed-axis gear transmission mechanism, and an output shaft 36.

In the second embodiment, except for the fixed-axis gear transmission mechanism, the rest of the structure is completely the same as that of the first embodiment, and the fixed-axis gear transmission mechanism of the second embodiment is different from the first embodiment in that the thirty-eighth gear 38 for controlling the third-gear transmission is meshed with the forty-fourth gear 44 (in the first embodiment, the thirty-eighth gear 38 is meshed with the fourth gear 4), and the rest of the structure is completely the same as that of the first embodiment.

Based on the above differences, in the transmission of each shift path of the loader hydraulic mechanical shunt transmission device described in the second embodiment, the forward hydraulic mechanical 1 gear, the forward hydraulic mechanical 2 gear, the forward mechanical 1 gear, the forward mechanical 2 gear, the reverse hydraulic mechanical 1 gear, the reverse hydraulic mechanical 2 gear, the reverse mechanical 1 gear, and the reverse mechanical 2 gear are completely the same as the transmission paths in the first embodiment, and the transmission paths of the forward hydraulic mechanical 3 gear, the forward mechanical 3 gear, the reverse hydraulic mechanical 3 gear, and the reverse mechanical 3 gear are different, and are respectively described below:

the forward hydraulic machine 3-speed path transmission is:

k₁clutch 11, k₂Clutch 17, k₆Clutch 39 and k₇Clutch 30 engaged, k₃Clutch 43, k₄Clutch 24, k₅Clutch 27 and k₈The clutch 32 is disengaged;

on the one hand, the hydraulic path transmits power: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁Clutch 11, from hydraulic variable displacement pumpThe input shaft 7 is transmitted to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 is transmitted to the hydraulic constant displacement motor 14, and then sequentially transmitted from the hydraulic constant displacement motor output shaft 15 to the motor₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are sequentially transmitted to the second planet carrier 20, the first ring gear 9 and the first planet gear set 8 through a hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the first sun gear 5 and the first planetary gear set 8 through the input shaft 1 and the mechanical shunt shaft 46;

the hydraulic path transmission power and the mechanical path transmission power are combined at the first carrier 6, and transmitted to k through the fourth gear 4, the forty-fourth gear 44, and the thirty-eighth gear 38 in this order₆Clutch 39, via a fortieth gear 40, transmits power to k₇The clutch 30 finally transmits power to the output shaft 36 via the thirty-first gear 31, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and thereby achieves power output.

The forward mechanical 3-gear path transmission is:

k₆clutch 39 and k₇Clutch 30 engaged, k₁Clutch 11, k₂Clutch 17, k₃Clutch 43, k₄Clutch 24, k₅Clutch 27 and k₈The clutch 32 is disengaged;

the engine input power is transmitted to the first sun gear 5, the first planetary gear set 8 and the first carrier 6 through the input shaft 1 and the mechanical split shaft 46, and then transmitted to k through the fourth gear 4, the forty-fourth gear 44 and the thirty-eighth gear 38 in sequence₆Clutch 39, via a fortieth gear 40, transmits power to k₇The clutch 30 finally transmits power to the output shaft 36 via the thirty-first gear 31, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and thereby achieves power output.

The reverse hydromechanical 3-gear path transfers:

k₁clutch 11, k₂Clutch 17, k₄Clutch 24, k₆Clutch 39 and k₈The clutch 32 is connectedIn the formula (i) k₃Clutch 43, k₅Clutch 27 and k₇The clutch 30 is disengaged;

on the one hand, the hydraulic path transmits power: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁The clutch 11 is transmitted from the input shaft 7 of the hydraulic variable pump to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 is transmitted to the constant displacement motor 14 and then transmitted to the motor k sequentially from the output shaft 15 of the constant displacement motor₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are sequentially transmitted to the second planet carrier 20, the first ring gear 9 and the first planet gear set 8 through a hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the first sun gear 5 and the first planetary gear set 8 through the input shaft 1 and the mechanical shunt shaft 46;

the hydraulic path transmission power and the mechanical path transmission power are combined at the first carrier 6, and transmitted to k through the fourth gear 4, the forty-fourth gear 44, and the thirty-eighth gear 38 in this order₆The clutch 39 transmits power to the gear k via a fortieth gear 40 and a fortieth gear 41 in this order₄The clutch 24, in turn, transmits power to k through the twenty-fifth gear 25, the twenty-ninth gear 29, and the thirty-fifth gear 35 in that order₈The clutch 32 finally transmits power to the output shaft 36 via the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and the power output is realized.

The reverse mechanical 3-gear path transmission is:

k₄clutch 24, k₆Clutch 39 and k₈Clutch 32 engaged, k₁Clutch 11, k₂Clutch 17, k₃Clutch 43, k₅Clutch 27 and k₇The clutch 30 is disengaged;

the engine input power is transmitted to the first sun gear 5, the first planetary gear set 8 and the first carrier 6 through the input shaft 1 and the mechanical split shaft 46, and then transmitted to k through the fourth gear 4, the forty-fourth gear 44 and the thirty-eighth gear 38 in sequence₆The clutch 39 passes through a fortieth gear 40 and a fortieth gear in this order41 transfer power to k₄The clutch 24, in turn, transmits power to k through the twenty-fifth gear 25, the twenty-ninth gear 29, and the thirty-fifth gear 35 in that order₈The clutch 32 finally transmits power to the output shaft 36 via the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and the power output is realized.

Example three:

as shown in fig. 16, the third embodiment discloses a hydraulic mechanical split transmission device of a loader, which includes a box 2, an input shaft 1, a split mechanism, a hydraulic transmission mechanism, a confluence mechanism, a hydraulic split shaft 45, a mechanical split shaft 46, a first intermediate shaft 28, a second intermediate shaft 33, a fixed-axis gear transmission mechanism and an output shaft 36.

In the third embodiment, except for the fixed-axis gear transmission mechanism, the rest of the structure is completely the same as that of the first embodiment, and the fixed-axis gear transmission mechanism of the second embodiment is different from that of the first embodiment in that k is used for controlling and realizing reverse transmission₈The clutch 32 is eliminated, and the thirty-fifth gear 35 is directly and coaxially fixed on the second intermediate shaft 33 (in the first embodiment, k is arranged between the thirty-fifth gear 35 and the second intermediate shaft 33₈The clutch 32).

Based on the above differences, in the transmission of each gear path of the loader hydraulic mechanical split transmission described in the third embodiment, the forward hydraulic mechanical 1 gear, the forward hydraulic mechanical 2 gear, the forward hydraulic mechanical 3 gear, the forward mechanical 1 gear, the forward mechanical 2 gear, and the forward mechanical 3 gear are completely the same as the transmission paths in the first embodiment, while the transmission paths of the reverse hydraulic mechanical 1 gear, the reverse hydraulic mechanical 2 gear, the reverse hydraulic mechanical 3 gear, the reverse mechanical 1 gear, and the reverse mechanical 3 gear are different, and the following descriptions are respectively given:

the reverse hydromechanical 1-gear path transmission is:

k₁clutch 11, k₂Clutch 17, k₃Clutch 43 and k₄Clutch 24 engaged, k₅Clutch 27, k₆Clutch 39 and k₇The clutch 30 is disengaged;

on the one hand, hydraulic circuitPower transmission: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁The clutch 11 is transmitted from the input shaft 7 of the hydraulic variable pump to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 is transmitted to the constant displacement motor 14 and then transmitted to the motor k sequentially from the output shaft 15 of the constant displacement motor₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are sequentially transmitted to the second planet carrier 20, the first ring gear 9 and the first planet gear set 8 through a hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the first sun gear 5 and the first planetary gear set 8 through the input shaft 1 and the mechanical shunt shaft 46;

the hydraulic path transmission power and the mechanical path transmission power are combined at the first carrier 6, and the power is transmitted to the gear k through the fourth gear 4 and the forty-fourth gear 44 in this order₃Clutch 43, which in turn transmits power to k via forty-first gear 41₄The clutch 24 finally transmits power to the output shaft 36 through the twenty-fifth gear 25, the twenty-ninth gear 29, the thirty-fifth gear 35, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and power output is realized.

The reverse hydromechanical 2-speed path is transferred as:

k₁clutch 11, k₂Clutch 17 and k₅Clutch 27 engaged, k₃Clutch 43, k₄Clutch 24, 27k₆Clutch 39 and k₇The clutch 30 is disengaged;

on the one hand, the hydraulic path transmits power: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁The clutch 11 is transmitted from the input shaft 7 of the hydraulic variable pump to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 is transmitted to the constant displacement motor 14 and then transmitted to the motor k sequentially from the output shaft 15 of the constant displacement motor₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are transmitted to the second carrier 20 through the hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the second sun gear 21 and the second planetary gear set 19 through the input shaft 1 and the mechanical split shaft 46;

according to the transmission characteristics of the planetary gear train, the second planet carrier 20, the second sun gear 21 and the second planetary gear set 19 drive the second gear ring 18 to move;

the hydraulic path transmission power and the mechanical path transmission power are combined at the second ring gear 18 and transmitted to k through the twenty-second and twenty-sixth gears 22 and 26 in order₅The clutch 27 then transmits power to the output shaft 36 via the twenty-fifth gear 25, the twenty-ninth gear 29, the thirty-fifth gear 35, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and power output is achieved.

The reverse hydromechanical 3-gear path transfers:

k₁clutch 11, k₂Clutch 17, k₄Clutch 24 and k₆Clutch 39k₈Clutch 32 engaged, k₃Clutch 43, k₅Clutch 27 and k₇The clutch 30 is disengaged;

on the one hand, the hydraulic path transmits power: the engine input power passes through the input shaft 1, the third gear 3, the tenth gear 10 and k₁The clutch 11 is transmitted from the input shaft 7 of the hydraulic variable pump to the hydraulic variable pump 12, and the power output from the hydraulic variable pump 12 is transmitted to the constant displacement motor 14 and then transmitted to the motor k sequentially from the output shaft 15 of the constant displacement motor₂The clutch 17, the sixteenth gear 16 and the twenty-third gear 23 are sequentially transmitted to the second planet carrier 20, the first ring gear 9 and the first planet gear set 8 through a hydraulic split shaft 45;

on the other hand, the mechanical path transmits power: the engine input power is transmitted to the first sun gear 5 and the first planetary gear set 8 through the input shaft 1 and the mechanical shunt shaft 46;

the hydraulic path transmission power and the mechanical path transmission power are combined at the first carrier 6 and transmitted to k through the fourth gear 4 and the thirty-eighth gear 38 in this order₆The clutch 39 transmits power to the gear k via a fortieth gear 40 and a fortieth gear 41 in this order₄The clutch 24 finally passes through a twenty-fifth gear 25,The twenty-ninth gear 29, the thirty-fifth gear 35, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 transmit power to the output shaft 36, achieving power output.

The reverse mechanical 1-gear path transmission is:

k₃clutches 43 and k₄Clutch 24 engaged, k₁Clutch 11, k₂Clutch 17, k₅Clutch 27, k₆Clutch 39 and k₇The clutch 30 is disengaged;

the engine input power is transmitted to the first sun gear 5, the first planetary gear set 8 and the first planet carrier 6 in sequence through the input shaft 1 and the mechanical shunt shaft 46, and then transmitted to the gear k in sequence through the fourth gear 4 and the fourth twelve gear 42₃Clutch 43 for transmitting power to k through the fourth eleventh gear 41₄The clutch 24 finally transmits power to the output shaft 36 through the twenty-fifth gear 25, the twenty-ninth gear 29, the thirty-fifth gear 35, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and power output is realized.

The reverse mechanical 2-gear path transmission is:

k₅clutch 27 engaged, k₁Clutch 11, k₂Clutch 17, k₃Clutch 43, k₄Clutch 24, k₆Clutch 39 and k₇The clutch 30 is disengaged;

the engine input power is transmitted to the second sun gear 21, the second planetary gear set 19 and the second ring gear 18 through the input shaft 1 and the mechanical split shaft 46, and is transmitted to the gear k through the twenty-second gear 22 and the twenty-sixth gear 26 in sequence₅The clutch 27 then transmits power to the output shaft 36 via the twenty-fifth gear 25, the twenty-ninth gear 29, the thirty-fifth gear 35, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and power output is achieved.

The reverse mechanical 3-gear path transmission is:

k₄clutch 24 and k₆Clutch 39 engaged, k₁Clutch 11, k₂Clutch 17, k₃Clutch 43, k₅Clutch device27 and k₇The clutch 30 is disengaged;

the engine input power is transmitted to the first sun gear 5, the first planetary gear set 8 and the first carrier 6 through the input shaft 1 and the mechanical split shaft 46, and then transmitted to the gear k through the fourth gear 4 and the thirty-eighth gear 38 in sequence₆The clutch 39 transmits power to the gear k via a fortieth gear 40 and a fortieth gear 41 in this order₄The clutch 24 finally transmits power to the output shaft 36 through the twenty-fifth gear 25, the twenty-ninth gear 29, the thirty-fifth gear 35, the second intermediate shaft 33, the thirty-fourth gear 34, and the thirty-seventh gear 37 in this order, and power output is realized.

Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

The above-described embodiments of the present invention should not be construed as limiting the scope of the present invention. Any other corresponding changes and modifications made according to the technical idea of the present invention should be included in the protection scope of the claims of the present invention.