CN215171926U - Gear box - Google Patents

Abstract

The utility model discloses a gear box, including main box body, input shaft, first output shaft, second output shaft, third output shaft, first main clutch, second main clutch, third main clutch, first brake clutch and second brake clutch, the input shaft is connected with first output shaft, second output shaft and third output shaft transmission respectively, first main clutch, second main clutch and third main clutch are installed inside the main box body, first brake clutch and second brake clutch are installed outside the main box body; in the technical scheme, the first brake clutch and the second brake clutch are arranged on the outer surface of the main box body in a backpack mode, so that the structure of parts in the main box body becomes compact, the volume of the main box body is further reduced, and the main box body is not required to be divided into an upper part, a middle part and a lower part; and further, the processing performance and the cost performance of the gearbox are improved.

Description

Gear box

Technical Field

The utility model relates to a mechanical transmission technical field especially relates to a gear box for boats and ships power is supplementary.

Background

During the driving of a ship, the ship is often required to have the capability of coping with various situations due to the diversity and complexity of river and marine environments, and thus, the ship needs a gear box with various output situations;

the existing gear box with various output conditions in the ship is generally used for outputting two cargo oil pumps and a generator, wherein each cargo oil pump and the generator are provided with an independent main clutch, and particularly, the cargo oil pump is also provided with an independent brake clutch; and the brake clutch and the main clutch are both arranged inside the gear box body and have two forms:

1) the brake clutch and the main clutch are coaxially distributed, but the length of the gearbox body of the gearbox is lengthened, other shafting supported in the gearbox body is also lengthened, and the weight of the whole gearbox is increased and the production cost is increased due to the fact that the shafting parts with the axial lengths correspondingly lengthened are added to the brake clutch part and the gearbox body;

2) the brake clutch and the main clutch are distributed in parallel, but the width (or height) of the box body is increased, the weight of the whole machine is increased due to the change of the box body, the bearing, the independent brake shaft and the like, and the production cost is directly increased.

In addition, the box body, the box cover, the end cover and the like are required to be completely disassembled when the two types of brake clutches are disassembled and maintained, if the brake clutches are arranged inside an input shaft system, the problem that the output tail shaft is required to be disassembled even the main engine is required to be solved, when the main engine is reset, the central lines of the main engine, the gear box and the tail shaft are required to be readjusted, the maintenance period is long, the efficiency is low, and the cost is high;

in addition, the gearbox usually needs an upper box body, a middle box body and a lower box body to solve the problem of the layout of the transmission device box body; the transmission chains in the gear box are more, the structure is complex, and the gear box has poor processing performance; these in turn contribute to the overall weight of the gearbox; and the processing performance of the gearbox is further reduced, the economic index of the gearbox is reduced, and the cost performance of the gearbox is lowered.

Disclosure of Invention

In order to solve the above problems, an object of the present invention is to overcome the disadvantages of the prior art, and to provide a gear box with short maintenance period, high efficiency and low cost.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

a gear box comprises a main box body, and an input shaft, a first output shaft, a second output shaft, a third output shaft, a first main clutch, a second main clutch, a third main clutch, a first brake clutch and a second brake clutch which are arranged on the main box body, wherein the input shaft is in transmission connection with the first output shaft, the second output shaft and the third output shaft respectively, and the input shaft, the first output shaft, the second output shaft and the third output shaft are distributed in parallel; first main clutch and first brake clutch all overlap and establish on first output shaft and be connected with first output shaft transmission, second main clutch and second brake clutch all overlap and establish on the second output shaft and be connected with second output shaft transmission, third main clutch overlaps and establishes on the third output shaft and be connected with third output shaft transmission, first main clutch, second main clutch and third main clutch are installed inside the main box, first brake clutch and second brake clutch are installed outside the main box.

Preferably, the second brake clutch has the same structure as the first brake clutch; the first main clutch, the second main clutch and the third main clutch are identical in structure.

Preferably, the first brake clutch comprises a small box body, a large end cover, a first pressure plate, a first piston, a plurality of annular first outer friction plates and a plurality of annular first inner friction plates, the large end cover is further provided with a first return spring and a small end cover, one end of the first output shaft extends into the small box body from the inside of the main box body, the first outer friction plates are in circumferential positioning axial movable fit with the small box body, the first inner friction plates are in circumferential positioning axial movable fit with the extending part of the first output shaft, the annular first inner friction plates and the annular first outer friction plates are alternately overlapped with each other, the first pressure plate and the first piston are respectively positioned at the inner side and the outer side of the first outer friction plates and the first inner friction plates, the first piston is provided with a braking position and a non-braking position, and the first return spring is used for driving the first piston to move from the braking position to the non-braking position, when the first piston is located at the braking position, the first piston presses the first outer friction plates and the first inner friction plates onto the first pressure plate.

Preferably, the small box body sequentially comprises a third ring body and a fourth ring body along the direction far away from the main box body, the diameter of the third ring body is larger than that of the fourth ring body, a plurality of mounting holes are formed in the end face of the third ring body, so that the small box body is fixedly mounted on the main box body through fasteners, and the large end cover is fixedly mounted on the fourth ring body through a plurality of fasteners;

the fourth ring is provided with a radial first through hole, the first output shaft is provided with an axial first blind hole, a radial first hole and a radial second hole, a plurality of radial second through holes are circumferentially distributed on the first spline groove, the first hole and the second hole are both communicated with the first blind hole, the first through hole is communicated with the first hole, the opening of the second hole is positioned at the first spline groove, and the first through hole, the first hole, part of the first blind hole and the second hole are matched to form a first lubricating oil channel of the first main clutch; then, the lubricating oil in the first lubricating oil channel is uniformly dispersed into a plurality of second inner friction plates and second outer friction plates through a plurality of second through holes;

be equipped with radial third through-hole on the fourth ring, be equipped with axial second blind hole on the first output shaft and still be equipped with radial third hole and fourth hole, the third through-hole communicates with each other with the third hole, the opening in fourth hole and second reset spring are located the both sides of second piston respectively, third through-hole, third hole, second blind hole and fourth hole cooperation form the first working oil passageway of first main clutch.

Preferably, the inner side wall of the fourth ring is in circumferential positioning axial sliding fit with the first outer friction plates through spline grooves, one end, extending out of the main box body, of the first output shaft is connected with a shaft sleeve through the spline grooves, and the first inner friction plates are in circumferential positioning axial sliding fit with the shaft sleeve;

an axial first gap is arranged on the end surface of the fourth ring body, the first gap comprises a first arc-shaped surface and a first connecting surface used for connecting the first arc-shaped surface and the inner side wall of the fourth ring body,

the fourth ring body is further provided with an axial fifth hole, one end of the fifth hole is communicated with the first through hole, the other end of the fifth hole is located on the first connecting surface, and the fifth hole is a second lubricating oil channel of the first brake clutch.

Preferably, the large end cover comprises an eighth ring body and a ninth ring body, the first piston comprises a fifth ring body, a first shaft body and a second shaft body in sequence along the direction far away from the main box body,

the diameter of the outer side wall of the fifth ring body is equal to that of the outer side wall of the first shaft body, the outer side wall of the fifth ring body and the outer side wall of the first shaft body are abutted against the inner side wall of the eighth ring body, and the second shaft body is located in the ninth ring body; one end of the first output shaft extends into the inner side of the fifth ring body and is separated from the eighth ring body by a gap, the first return spring is sleeved on the second shaft body,

and a radial fourth through hole is formed in the ninth ring body, and the fourth through hole is a second working oil channel of the first brake clutch.

Preferably, the clutch is further provided with a first idler shaft, the input shaft is sleeved with first transmission teeth in a hot manner, the first idler shaft is sleeved with second transmission teeth in a hot manner, the first output shaft is sleeved with third transmission teeth in a hot manner, the first main clutch comprises a first gear ring, a second return spring, a second piston, a second pressure plate, a plurality of annular second outer friction plates and a plurality of annular second inner friction plates, the first gear ring is sleeved on the first output shaft in a hot manner, the second outer friction plates are in circumferential positioning axial movable fit with the first gear ring, the second inner friction plates are in circumferential positioning axial movable fit with the third transmission teeth, the plurality of annular second inner friction plates and the plurality of annular second friction plates are alternately overlapped with each other, the second return spring and the second piston are sleeved on the first output shaft, the second pressure plate is mounted on the first gear ring and is sleeved on the third transmission teeth in an empty manner, the second piston and the second pressure plate are respectively positioned on two sides of the alternately overlapped second outer friction plates and the first inner friction plates, the second return spring is located between the first output shaft and the third transmission gear, and the second piston is used for pressing the second outer friction plate and the first inner friction plate on the pressure plate.

Preferably, the third transmission gear is mounted on the upper box body and the lower box body through a sixth self-aligning roller bearing and a fourth cylindrical roller bearing; the first output shaft is provided with a third self-aligning roller bearing, a fourth cylindrical roller bearing, a sixth self-aligning roller bearing and a first cylindrical roller bearing in sequence from the cargo oil pump to the first brake clutch;

be equipped with first ring body, first gear portion and second ring body on the third driving gear in proper order, fourth cylindrical roller bearing and sixth self-aligning roller bearing tight cover respectively on first ring body and second ring body, first gear portion and the meshing of second driving gear, still be equipped with first spline groove on the first ring body, fourth cylindrical roller bearing is located between first spline groove and the first gear portion, friction disc passes through first spline groove and third driving gear circumference location axial clearance fit in a plurality of seconds.

Preferably, the second piston comprises a sixth ring body and a seventh ring body from inside to outside, an annular first groove is further formed between the sixth ring body and the seventh ring body, the sixth ring body is higher than the seventh ring body, the sixth ring body is used for pushing the second return spring, and the seventh ring body is used for pushing the second outer friction plate and the second inner friction plate.

Preferably, the gearbox is further provided with a second idler shaft, a fourth transmission gear is sleeved on the second idler shaft in a hot manner, a fifth transmission gear is sleeved on the second output shaft, and the fifth transmission gear is meshed with the fourth transmission gear;

the third idler shaft is sleeved with sixth transmission teeth in a hot manner, the fourth idler shaft is sleeved with seventh transmission teeth in a hot manner, the fifth idler shaft is sleeved with eighth transmission teeth and ninth transmission teeth in a hot manner, the third output shaft is sleeved with tenth transmission teeth, the sixth transmission teeth are meshed with the fifth transmission teeth, the seventh transmission teeth are meshed with the sixth transmission teeth, the eighth transmission teeth are meshed with the seventh transmission teeth, and the ninth transmission teeth are meshed with the tenth transmission teeth.

The utility model has the advantages that:

1) in the technical scheme, the first output shaft is used for being in transmission connection with the first cargo oil pump, the second output shaft is used for being in transmission connection with the second cargo oil pump, and the third output shaft is used for being in transmission connection with the generator; thus, due to the presence of the first main clutch, the second main clutch and the third main clutch; the first output shaft, the second output shaft and the third output shaft can also independently adjust the rotating speed, and meanwhile, due to the first brake clutch and the second brake clutch, the first cargo oil pump and the second cargo oil pump can also have the condition of non-working, so that the complex condition of the ship in the running process is adapted;

2) in the technical scheme, the first brake clutch and the second brake clutch are arranged on the outer surface of the main box body in a backpack mode, so that the structure of parts in the main box body becomes compact, the volume of the main box body is further reduced, and the main box body is not divided into an upper part, a middle part and a lower part; thereby improving the processing performance and the cost performance of the gear box;

3) among this technical scheme, first brake clutch and second brake clutch also only need pull down little box, big end cover and little end cover when maintenance and maintenance, and are very convenient.

Drawings

FIG. 1 is a schematic view of the transmission of the gear box of the present invention;

FIG. 2 is a schematic diagram of an output structure of the gearbox of the present invention;

fig. 3 is a schematic view of a first brake clutch according to the present invention;

fig. 4 is a schematic view of a third gear of the present invention;

fig. 5 is a schematic view of a second piston of the present invention;

fig. 6 is a schematic view of a first piston of the present invention;

fig. 7 is a partial enlarged view of a portion a in fig. 3.

Description of reference numerals: 1. a main box body; 101. an input shaft; 102. a first output shaft; 103. a second output shaft; 104. a third output shaft; 2. a first main clutch; 3. a second main clutch; 4. a third main clutch; 5. a first brake clutch; 6. a second brake clutch; 50. a small box body; 51. a large end cap; 52. a first platen; 53. a first piston; 54. a first outer friction plate; 55. a first inner friction plate; 56. a first return spring; 57. a small end cap; 105. a first idler shaft; 106. a first drive tooth; 107. a second gear; 108. a third gear; 20. a first ring gear; 21. a second return spring; 22. a second piston; 23. a second platen; 24. a second outer friction plate; 25. a second inner friction plate; 1080. a first ring body; 1081. a first gear portion; 1082. a second ring body; 220. a sixth ring body; 221. a seventh ring body; 222. a first groove; 500. a third ring body; 501. a fourth ring body; 502. a first through hole; 1020. a first blind hole; 1021. a first hole; 1022. a second hole; 1083. a second through hole; 503. a third through hole; 1023. a second blind hole; 1024. a third aperture; 1025. a fourth aperture; 58. an oil seal bushing; 580. a fifth through hole; 581. a sixth through hole; 504. a first arc-shaped surface; 505. a first connection face; 506. a fifth aperture; 510. an eighth ring body; 511. a ninth ring body; 530. a fifth ring body; 531. a first shaft body; 532. a second shaft body; 512. a fourth via hole; 59. a circlip for the first shaft; 109. a second idler shaft; 110. a fourth gear; 111. a fifth gear; 112. a third idler shaft; 113. a fourth idler shaft; 114. a fifth idler shaft; 115. a sixth gear; 116. a seventh gear; 117. an eighth gear; 118. a ninth gear; 119. a tenth gear tooth; 120. a first oil pump; 121. a second oil pump; 122. a first cargo oil pump; 123. a second cargo oil pump; 124. a generator; 60. and a shaft sleeve.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present invention, and should not be construed as limiting the present invention.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and to simplify the description, but do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore should not be construed as limiting the present invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, unless otherwise specified, "a plurality" means two or more unless explicitly defined otherwise.

In the present invention, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

In the present disclosure, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may comprise direct contact between the first and second features, or may comprise contact between the first and second features not directly. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.

The first embodiment is as follows:

a gearbox as shown in fig. 1 and 2 is mainly used for providing power output for a plurality of cargo oil pumps and a generator 124 in a ship, wherein each cargo oil pump and the generator 124 can work independently without being interfered by other cargo oil pumps or generators 124.

In the embodiment, the gearbox comprises a main box body 1, and an input shaft 101, a first output shaft 102, a second output shaft 103, a third output shaft 104, a first main clutch 2, a second main clutch 3, a third main clutch 4, a first brake clutch 5 and a second brake clutch 6 which are arranged on the main box body 1, wherein the input shaft 101 is in transmission connection with the first output shaft 102, the second output shaft 103 and the third output shaft 104 respectively, and the input shaft 101, the first output shaft 102, the second output shaft 103 and the third output shaft 104 are distributed in parallel; the first main clutch 2 and the first brake clutch 5 are sleeved on the first output shaft 102 and are in transmission connection with the first output shaft 102, the second main clutch 3 and the second brake clutch 6 are sleeved on the second output shaft 103 and are in transmission connection with the second output shaft 103, the third main clutch 4 is sleeved on the third output shaft 104 and is in transmission connection with the third output shaft 104, the first main clutch 2, the second main clutch 3 and the third main clutch 4 are installed inside the main box body 1, and the first brake clutch 5 and the second brake clutch 6 are installed outside the main box body 1;

as shown in fig. 3, the first brake clutch 5 includes a small case 50, a large end cap 51, a first pressure plate 52, a first piston 53, a plurality of annular first outer friction plates 54, and a plurality of annular first inner friction plates 55, which are mounted on the small case 50, a first return spring 56 and a small end cap 57 are further mounted on the large end cap 51, one end of the first output shaft 102 extends from the inside of the main case 1 to the inside of the small case 50, the first outer friction plates 54 are circumferentially and axially movably engaged with the small case 50, the first inner friction plates 55 are circumferentially and axially movably engaged with the extending portion of the first output shaft 102, the plurality of annular first inner friction plates 55 and the plurality of annular first outer friction plates 54 are alternately stacked on each other, the first pressure plate 52 and the first piston 53 are respectively located at the inner side and the outer side of the plurality of first outer friction plates 54 and the plurality of first inner friction plates 55, the first piston 53 has a braking position and a non-braking position, the first return spring 56 is used for driving the first piston 53 to move from the braking position to the non-braking position, and when the first piston 53 is located at the braking position, the first piston 53 presses the plurality of first outer friction plates 54 and the plurality of first inner friction plates 55 against the first pressure plate 52;

the second brake clutch 6 has the same structure as the first brake clutch 5; and will not be described in detail herein.

It should be noted that the first output shaft 102 is configured to be in transmission connection with a first cargo oil pump 122, the second output shaft 103 is configured to be in transmission connection with a second cargo oil pump 123, and the third output shaft 104 is configured to be in transmission connection with a generator 124; in this way, due to the presence of first main clutch 2, second main clutch 3 and third main clutch 4; the first output shaft 102, the second output shaft 103 and the third output shaft 104 can also independently adjust the rotating speed, and meanwhile, due to the first brake clutch 5 and the second brake clutch 6, the first cargo oil pump 122 and the second cargo oil pump 123 can also have the condition of non-working, so that the complex condition of the ship in the running process is adapted;

in particular, since the first brake clutch 5 and the second brake clutch 6 are mounted on the outer surface of the main body case 1 in the form of a backpack, it is possible to make the structure of the components inside the main body case 1 compact, thereby reducing the volume of the main body case 1 and making the main body case 1 not to be subdivided into upper, middle and lower portions; thereby improving the processing performance and the cost performance of the gear box;

in addition, when the first brake clutch 5 and the second brake clutch 6 are maintained, only the small box 50 and the end covers need to be detached, which is very convenient.

It should be noted that in other embodiments, other output shafts may be provided for connection to other cargo oil pumps, and likewise, the output shafts may be provided with a master clutch and a brake clutch.

Preferably, the main box body 1 is composed of an upper box body and a lower box body which are of an upper cross-sectional structure and a lower cross-sectional structure, and the input shaft 101 is installed on the upper box body and the lower box body through a first self-aligning roller bearing and a second self-aligning roller bearing;

the first output shaft 102 is mounted on the upper box body and the lower box body through a third self-aligning roller bearing and a first cylindrical roller bearing;

the second output shaft 103 is mounted on the upper box body and the lower box body through a fourth self-aligning roller bearing and a second cylindrical roller bearing;

the third output shaft 104 is mounted on the upper case and the lower case through a fifth self-aligning roller bearing and a third cylindrical roller bearing.

In this embodiment, a first idler shaft 105 is further provided, a first transmission tooth 106 is sleeved on the input shaft 101, a second transmission tooth 107 is sleeved on the first idler shaft 105, a third transmission tooth 108 is sleeved on the first output shaft 102, the first main clutch 2 includes a first gear ring 20, a second return spring 21, a second piston 22, a second pressure plate 23, a plurality of annular second outer friction plates 24 and a plurality of annular second inner friction plates 25, the first gear ring 20 is sleeved on the first output shaft 102, the second outer friction plates 24 are axially and movably matched with the first gear ring 20 in a circumferential positioning manner, the second inner friction plates 25 are axially and movably matched with the third transmission tooth 108 in a circumferential positioning manner, the plurality of annular second inner friction plates 25 and the plurality of annular second friction plates are alternately stacked, the second return spring 21 and the second piston 22 are sleeved on the first output shaft 102, the second pressure plate 23 is mounted on the first gear ring 20 and is freely sleeved on the third transmission tooth 108, the second pressure plate 23 and the second piston 22 are respectively positioned on both sides of the second outer friction plates 24 and the first inner friction plates 55 which are alternately stacked, the second return spring 21 is positioned between the first output shaft 102 and the third driving gear 108, and the second piston 22 is used for pressing the second outer friction plates 24 and the first inner friction plates 55 on the pressure plate.

Preferably, the third transmission gear 108 is mounted on the upper box and the lower box through a sixth self-aligning roller bearing and a fourth cylindrical roller bearing; wherein, the first output shaft 102 is sequentially provided with a third self-aligning roller bearing, a fourth cylindrical roller bearing, a sixth self-aligning roller bearing and a first cylindrical roller bearing from the cargo oil pump to the first brake clutch 5.

As shown in fig. 4, the third transmission gear 108 is sequentially provided with a first ring body 1080, a first gear portion 1081 and a second ring body 1082, the fourth cylindrical roller bearing and the sixth self-aligning roller bearing are respectively and tightly sleeved on the first ring body 1080 and the second ring body 1082, the first gear portion 1081 is meshed with the second transmission gear 107, the first ring body 1080 is further provided with a first spline groove, the fourth cylindrical roller bearing is located between the first spline groove and the first gear portion 1081, and the plurality of second inner friction plates 25 are axially movably matched with the third transmission gear 108 in the circumferential positioning direction through the first spline groove.

Preferably, a circlip for the first hole 1021 is further provided, the circlip for the first hole 1021 is attached to the inner side wall of the first ring gear 20, and the circlip for the first hole 1021 is used to prevent the second pressure plate 23 from moving in a direction away from the second piston 22.

As shown in fig. 5, the second piston 22 includes a sixth ring body 220 and a seventh ring body 221 from inside to outside, an annular first groove 222 is further provided between the sixth ring body 220 and the seventh ring body 221, the sixth ring body 220 is higher than the seventh ring body 221, the sixth ring body 220 is used for pushing the second return spring 21, and the seventh ring body 221 is used for pushing the second outer friction plate 24 and the second inner friction plate 25; wherein the first recess 222 is primarily for preventing the second piston 22 from abutting the third gear 108.

In this embodiment, the small box 50 sequentially includes a third ring 500 and a fourth ring 501 along a direction away from the main box 1, the diameter of the third ring 500 is greater than that of the fourth ring 501, a plurality of mounting holes are formed in the end face of the third ring 500, so that the small box 50 is fixedly mounted on the main box 1 through fasteners, and the large end cover 51 is fixedly mounted on the fourth ring 501 through a plurality of fasteners.

In this embodiment, a radial first through hole 502 is formed in the fourth ring 501, an axial first blind hole 1020 and a radial first hole 1021 and a radial second hole 1022 are further formed in the first output shaft 102, a plurality of radial second through holes 1083 are circumferentially distributed on the first spline groove, the first hole 1021 and the second hole 1022 are both communicated with the first blind hole 1020, the first through hole 502 is communicated with the first hole 1021, an opening of the second hole 1022 is located at the first spline groove, and the first through hole 502, the first hole 1021, a part of the first blind hole 1020 and the second hole 1022 are matched to form a first lubricating oil passage of the first main clutch 2; then, the lubricating oil in the first lubricating oil channel is uniformly dispersed into the plurality of second inner friction plates 25 and the plurality of second outer friction plates 24 through the plurality of second through holes 1083.

In this embodiment, a radial third through hole 503 is arranged on the fourth ring 501, an axial second blind hole 1023 and a radial third hole 1024 and a radial fourth hole 1025 are further arranged on the first output shaft 102, the third through hole 503 is communicated with the third hole 1024, an opening of the fourth hole 1025 and the second return spring 21 are respectively located on two sides of the second piston 22, and the third through hole 503, the third hole 1024, the second blind hole 1023 and the fourth hole 1025 are matched to form a first working oil channel of the first main clutch 2.

Further preferably, an oil sealing bush 58 is further provided, and the oil sealing bush 58 is tightly sleeved on the first output shaft 102 and abuts against the inner side wall of the fourth ring 501; a fifth through hole 580 and a sixth through hole 581 which are radial are arranged on the oil seal bushing 58, and two ends of the fifth through hole 580 are respectively communicated with the first through hole 502 and the first hole 1021; two ends of the sixth through hole 581 are respectively communicated with the third through hole 503 and the third through hole 1024; this arrangement is because if the through hole on the fourth ring 501 is directly communicated with the radial hole on the first output shaft 102; easily causing oil leakage.

It is noted that the open ends of the first blind hole 1020 and the second blind hole 1023 are in a sealed state.

In this embodiment, the inner side wall of the fourth ring 501 is in circumferential positioning axial sliding fit with the first outer friction plates 54 through spline grooves, one end of the first output shaft 102, which extends out of the main case 1, is connected with a shaft sleeve 60 through spline grooves, and the first inner friction plates 55 are in circumferential positioning axial sliding fit with the shaft sleeve 60;

as shown in fig. 7, an axial first notch is provided on an end surface of the fourth ring 501, the first notch includes a first arc surface 504 and a first connecting surface 505 for connecting the first arc surface 504 and an inner side wall of the fourth ring 501,

the fourth ring 501 is further provided with an axial fifth hole 506, one end of the fifth hole 506 is communicated with the first through hole 502, the other end of the fifth hole 506 is located on the first connection surface 505, and the fifth hole 506 is a second lubricating oil channel of the first brake clutch 5.

In this embodiment, the large end cap 51 includes an eighth ring 510 and a ninth ring 511, as shown in fig. 6, the first piston 53 includes a fifth ring 530, a first shaft 531 and a second shaft 532 in sequence along the direction away from the main housing 1,

the diameter of the outer side wall of the fifth ring body 530 is equal to that of the outer side wall of the first shaft body 531, the outer side wall of the fifth ring body 530 and the outer side wall of the first shaft body 531 both abut against the inner side wall of the eighth ring body 510, and the second shaft body 532 is located in the ninth ring body 511; one end of the first output shaft 102 extends into the inner side of the fifth ring member 530 and is spaced from the eighth ring member 510 by a gap, the first return spring 56 is sleeved on the second ring member 532,

the ninth ring body 511 is provided with a radial fourth through hole 512, and the fourth through hole 512 is a second working oil passage of the first brake clutch 5.

More preferably, a first shaft circlip 59 is further mounted on the second shaft 532, one end of the first return spring 56 abuts against the sixth ring member 220, and the other end of the first return spring 56 abuts against the first shaft circlip 59.

It should be noted that the clearance between the first output shaft 102 and the sixth ring member 220 should be greater than or equal to the distance between the first piston 53 moving from the apply position to the non-apply position.

In this embodiment, a second idler shaft 109 is further provided, a fourth transmission gear 110 is sleeved on the second idler shaft 109, a fifth transmission gear 111 is sleeved on the second output shaft 103, and the fifth transmission gear 111 is meshed with the fourth transmission gear 110; the second main clutch 3 and the first main clutch 2 have the same structure, the fifth transmission gear 111 and the second main clutch 3 are also matched with the third transmission gear 108 and the first main clutch 2, and the second brake clutch 6 and the first brake clutch 5 have the same structure, and therefore, detailed description is omitted.

In this embodiment, a third idler shaft 112, a fourth idler shaft 113 and a fifth idler shaft 114 are further provided, a sixth driving tooth 115 is sleeved on the third idler shaft 112 in a hot manner, a seventh driving tooth 116 is sleeved on the fourth idler shaft 113 in a hot manner, an eighth driving tooth 117 and a ninth driving tooth 118 are sleeved on the fifth idler shaft 114 in a hot manner, a tenth driving tooth 119 is sleeved on the third output shaft 104 in a hot manner, the sixth driving tooth 115 is meshed with the fifth driving tooth 111, the seventh driving tooth 116 is meshed with the sixth driving tooth 115, the eighth driving tooth 117 is meshed with the seventh driving tooth 116, and the ninth driving tooth 118 is meshed with the tenth driving tooth 119; the third main clutch 4 and the first main clutch 2 have the same structure, and the third main clutch 4 and the tenth gear 119 are also matched in the same way as the third gear 108 and the first main clutch 2, and will not be described in detail here.

It is worth mentioning that the main purpose of providing a plurality of idler shafts is to make the whole gearbox more stable.

Further preferably, the diameter of the eighth gear tooth 117 is smaller than the diameter of the ninth gear tooth 118; thereby making the rotational speed of the third output shaft 104 greater than the rotational speed of the second output shaft 103.

It should be noted that the second idler shaft 109, the third idler shaft 112, the fourth idler shaft 113 and the fifth idler shaft 114 are all mounted on the upper case and the lower case through two self-aligning roller bearings.

In this embodiment, a first oil pump 120 and a second oil pump 121 are further provided, the first oil pump 120 is used for sucking the working oil and the lubricating oil in the first main clutch 2, the second main clutch 3, the first brake clutch 5 and the second brake clutch 6, and the second oil pump 121 is used for sucking the working oil and the lubricating oil in the second main clutch 3, the third main clutch 4 and the second brake clutch 6.

In the present embodiment, the first cargo oil pump 122, the second cargo oil pump 123 and the generator 124 are respectively operated by the first control valve, the second control valve and the third control valve; the specific process is as follows:

when the first control valve is in the stop position, the hydraulic control system directly washes out the working oil of the first main clutch 2 and the working oil of the first brake clutch 5 on the first output shaft 102 through the first oil pump 120, the first inner friction plate 55 and the first outer friction plate 54 are separated from each other, the third transmission gear 108 is sleeved on the first output shaft 102 in an empty manner, and the first cargo oil pump 122 does not work and does not brake;

when the first control valve is in the working position, the hydraulic control system guides the working oil into the first main clutch 2 along the first working oil channel, pushes the second piston 22 to move, and further enables the plurality of second inner friction plates 25 and the plurality of second outer friction plates 24 to be tightly pressed on the second pressure plate 23, so that the third transmission teeth 108 rotate synchronously with the first output shaft 102, and the first cargo oil pump 122 works;

when the first control valve is in a braking position, the hydraulic control system guides the working oil into the first brake clutch 5 along the second working oil channel to push the first piston 53 to move, so that the first inner friction plates 55 and the first outer friction plates 54 are pressed on the first pressure plate 52, the first output shaft 102 stops rotating, and the first cargo oil pump 122 performs braking operation;

it is worth noting that the second control valve also has "stop", "work" and "brake" positions, the working process of which is identical to that described above and will not be described in detail herein;

the second control valve has only "off" and "on" positions, but the operation is consistent with that described above and will not be described in detail here.

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 do not necessarily 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.

Although embodiments of the present invention have been shown and described, it is to be understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that changes, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art without departing from the principles and spirit of the present invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (10)

1. A gearbox is characterized by comprising a main box body (1), an input shaft (101), a first output shaft (102), a second output shaft (103), a third output shaft (104), a first main clutch (2), a second main clutch (3), a third main clutch (4), a first brake clutch (5) and a second brake clutch (6), wherein the input shaft (101) is in transmission connection with the first output shaft (102), the second output shaft (103) and the third output shaft (104), and the input shaft (101), the first output shaft (102), the second output shaft (103) and the third output shaft (104) are distributed in parallel; first main clutch (2) and first brake clutch (5) all overlap and establish on first output shaft (102) and be connected with first output shaft (102) transmission, second main clutch (3) and second brake clutch (6) all overlap and establish on second output shaft (103) and be connected with second output shaft (103) transmission, third main clutch (4) overlap and establish on third output shaft (104) and be connected with third output shaft (104) transmission, install inside main box (1) first main clutch (2), second main clutch (3) and third main clutch (4), install outside main box (1) first brake clutch (5) and second brake clutch (6).

2. A gearbox according to claim 1 in which the second brake clutch (6) is of the same construction as the first brake clutch (5); the first main clutch (2), the second main clutch (3) and the third main clutch (4) are identical in structure.

3. A gearbox according to claim 1, characterised in that a first idler shaft (105) is provided, first transmission teeth (106) are shrink-fitted on said input shaft (101), second transmission teeth (107) are shrink-fitted on said first idler shaft (105), third transmission teeth (108) are shrink-fitted on said first output shaft (102), said first main clutch (2) comprises a first ring gear (20), a second return spring (21), a second piston (22), a second pressure plate (23), a plurality of annular second outer friction plates (24) and a plurality of annular second inner friction plates (25), said first ring gear (20) is shrink-fitted on said first output shaft (102), said second outer friction plates (24) are axially movably fitted with said first ring gear (20) in a circumferential positioning manner, and said second inner friction plates (25) are axially movably fitted with said third transmission teeth (108) in a circumferential positioning manner, a plurality of annular second inner friction plates (25) and a plurality of annular second friction plates are alternately overlapped with each other, a second return spring (21) and a second piston (22) are sleeved on the first output shaft (102), a second pressure plate (23) is installed on the first gear ring (20) and is sleeved on the third transmission gear (108) in an empty mode, the second pressure plate (23) and the second piston (22) are located on two sides of the second outer friction plates (24) and the first inner friction plates (55) which are alternately overlapped, the second return spring (21) is located between the first output shaft (102) and the third transmission gear (108), and the second piston (22) is used for pressing the second outer friction plates (24) and the first inner friction plates (55) on the first output shaft.

4. A gearbox according to claim 3, characterised in that the third driving gear (108) is mounted on the upper and lower housings by means of a sixth self-aligning roller bearing and a fourth cylindrical roller bearing; the first output shaft (102) is sequentially provided with a third self-aligning roller bearing, a fourth cylindrical roller bearing, a sixth self-aligning roller bearing and a first cylindrical roller bearing from the cargo oil pump to the first brake clutch (5);

be equipped with first ring body (1080), first gear portion (1081) and second ring body (1082) in proper order on third transmission tooth (108), fourth cylindrical roller bearing and sixth self-aligning roller bearing tightly overlap respectively on first ring body (1080) and second ring body (1082), first gear portion (1081) and second transmission tooth (107) meshing, still be equipped with first spline groove on first ring body (1080), fourth cylindrical roller bearing is located between first spline groove and first gear portion (1081), and friction disc (25) are through first spline groove and third transmission tooth (108) circumference location axial clearance fit in a plurality of seconds.

5. The gearbox according to claim 3, characterized in that the second piston (22) comprises a sixth ring body (220) and a seventh ring body (221) from inside to outside, an annular first groove (222) is further formed between the sixth ring body (220) and the seventh ring body (221), the sixth ring body (220) is higher than the seventh ring body (221), the sixth ring body (220) is used for pushing the second return spring (21), and the seventh ring body (221) is used for pushing the second outer friction plate (24) and the second inner friction plate (25).

6. A gearbox according to claim 4 in which the first brake clutch (5) comprises a small case (50) and a large end cap (51), a first pressure plate (52), a first piston (53), a plurality of annular first outer friction plates (54) and a plurality of annular first inner friction plates (55) mounted on the small case (50), a first return spring (56) and a small end cap (57) are mounted on the large end cap (51), one end of the first output shaft (102) extends from within the main case (1) into the small case (50), the first outer friction plates (54) are circumferentially located and axially movably engaged with the small case (50), the first inner friction plates (55) are circumferentially located and axially movably engaged with the extending portion of the first output shaft (102), the plurality of annular first inner friction plates (55) and the plurality of annular first outer friction plates (54) are alternately stacked on each other, the first pressure plate (52) and the first piston (53) are respectively located on the inner side and the outer side of a plurality of first outer friction plates (54) and a plurality of first inner friction plates (55), the first piston (53) is provided with a braking position and a non-braking position, the first return spring (56) is used for driving the first piston (53) to move from the braking position to the non-braking position, and when the first piston (53) is located at the braking position, the first piston (53) presses the plurality of first outer friction plates (54) and the plurality of first inner friction plates (55) on the first pressure plate (52).

7. The gearbox according to claim 6, characterized in that the small box body (50) comprises a third ring body (500) and a fourth ring body (501) in sequence along a direction away from the main box body (1), the diameter of the third ring body (500) is larger than that of the fourth ring body (501), a plurality of mounting holes are formed in the end face of the third ring body (500), the small box body (50) is fixedly mounted on the main box body (1) through fasteners, and the large end cover (51) is fixedly mounted on the fourth ring body (501) through a plurality of fasteners;

a radial first through hole (502) is formed in the fourth ring body (501), an axial first blind hole (1020) and a radial first hole (1021) and a radial second hole (1022) are formed in the first output shaft (102), a plurality of radial second through holes (1083) are circumferentially distributed on the first spline groove, the first hole (1021) and the second hole (1022) are communicated with the first blind hole (1020), the first through hole (502) is communicated with the first hole (1021), an opening of the second hole (1022) is located at the first spline groove, and the first through hole (502), the first hole (1021), a part of the first blind hole (1020) and the second hole (1022) are matched to form a first lubricating oil channel of the first main clutch (2); then, the lubricating oil in the first lubricating oil channel is uniformly dispersed into a plurality of second inner friction plates (25) and second outer friction plates (24) through a plurality of second through holes (1083);

be equipped with radial third through-hole (503) on fourth ring body (501), be equipped with axial second blind hole (1023) and still be equipped with radial third hole (1024) and fourth hole (1025) on first output shaft (102), third through-hole (503) communicate with each other with third hole (1024), the opening and second reset spring (21) of fourth hole (1025) are located the both sides of second piston (22) respectively, third through-hole (503), third hole (1024), second blind hole (1023) and fourth hole (1025) cooperation form the first working oil passageway of first main clutch (2).

8. A gearbox according to claim 7, characterized in that the inner side wall of said fourth ring body (501) is in circumferential positioning axial sliding fit with a plurality of first outer friction plates (54) through spline grooves, one end of said first output shaft (102) extending out of said main case (1) is connected with a shaft sleeve (60) through spline grooves, and a plurality of first inner friction plates (55) are in circumferential positioning axial sliding fit with the shaft sleeve (60);

an axial first gap is arranged on the end surface of the fourth ring body (501), the first gap comprises a first arc-shaped surface (504) and a first connecting surface (505) used for connecting the first arc-shaped surface (504) and the inner side wall of the fourth ring body (501),

the fourth ring body (501) is further provided with an axial fifth hole (506), one end of the fifth hole (506) is communicated with the first through hole (502), the other end of the fifth hole (506) is located on the first connecting surface (505), and the fifth hole (506) is a second lubricating oil channel of the first brake clutch (5).

9. A gearbox according to claim 7 in which said large end cap (51) includes an eighth ring (510) and a ninth ring (511), said first piston (53) includes a fifth ring (530), a first shaft body (531) and a second shaft body (532) in sequence along the direction away from the main housing (1),

the diameter of the outer side wall of the fifth ring body (530) is equal to that of the outer side wall of the first shaft body (531), the outer side wall of the fifth ring body (530) and the outer side wall of the first shaft body (531) are abutted against the inner side wall of the eighth ring body (510), and the second shaft body (532) is located in the ninth ring body (511); one end of the first output shaft (102) extends into the inner side of the fifth ring body (530) and is separated from the eighth ring body (510) by a gap, the first return spring (56) is sleeved on the second shaft body (532),

and a radial fourth through hole (512) is formed in the ninth ring body (511), and the fourth through hole (512) is a second working oil channel of the first brake clutch (5).

10. A gearbox according to claim 1, characterised in that a second idler shaft (109) is provided, a fourth driving gear (110) is shrink-fitted on the second idler shaft (109), a fifth driving gear (111) is shrink-fitted on the second output shaft (103), and the fifth driving gear (111) is meshed with the fourth driving gear (110);

the transmission device is characterized by further comprising a third idler shaft (112), a fourth idler shaft (113) and a fifth idler shaft (114), sixth transmission teeth (115) are sleeved on the third idler shaft (112) in a hot sleeved mode, seventh transmission teeth (116) are sleeved on the fourth idler shaft (113), eighth transmission teeth (117) and ninth transmission teeth (118) are sleeved on the fifth idler shaft (114) in a hot sleeved mode, tenth transmission teeth (119) are sleeved on the third output shaft (104), the sixth transmission teeth (115) are meshed with the fifth transmission teeth (111), the seventh transmission teeth (116) are meshed with the sixth transmission teeth (115), the eighth transmission teeth (117) are meshed with the seventh transmission teeth (116), and the ninth transmission teeth (118) are meshed with the tenth transmission teeth (119).

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