Clutch biased gearbox and tractor using the same

Abstract

The utility model discloses a clutch bias formula gearbox and use the tractor of this gearbox relates to power transmission technical field. Wherein clutch bias formula gearbox includes the box, and the transmission assembly is installed in the box, and the power input shaft is installed on the box, and the lateral installation of transmission assembly is installed in the box in the wet clutch assembly, and the wet clutch assembly with transmission assembly forms parallel arrangement, power piece in the wet clutch assembly is connected with power input shaft power through the clutch power input mechanism, and the driven part in the wet clutch assembly is connected with transmission assembly power through the clutch power output mechanism. The utility model realizes more friction plate configuration in the clutch, is favorable for reducing oil pressure and improves the torque transmission capacity, is favorable for improving gear shifting comfort, and is favorable for prolonging clutch service life and improving maintenance convenience.

Description

Technical Field

[0001] This utility model relates to the field of power transmission technology, and in particular to a clutch-biased gearbox and a tractor using the gearbox. Background Technology

[0002] Tractors are currently the mainstream power equipment in agricultural machinery. Their transmission system includes components such as clutches and gearboxes. The gearbox is used to shift power output, while the clutch is used to engage and disengage power. Due to the complexity of farmland operations, the gearbox needs to switch gears in various operating scenarios, such as low-speed high-torque traction, medium-to-high-speed driving, and heavy-load starting. The quality of the clutch's engagement and disengagement performance directly affects the comfort and reliability of gear shifting operations.

[0003] Currently, wet clutches are commonly used in medium and high-power tractors. These wet clutches utilize multiple friction plates. These plates are pressed together by a piston driven by hydraulic pressure, achieving power engagement. Once the piston disengages, the clamping force between the friction plates disappears, disengaging the power. Therefore, the smoothness and reliability of the multi-plate engagement are crucial factors affecting the power transmission performance of wet clutches.

[0004] Currently, wet clutches are all integrated into the transmission, and are mostly designed on the transmission's input shaft. Due to the limited installation space in the transmission, the length of the input shaft is limited, thus restricting the placement space of the wet clutch. It can only accommodate a maximum of 4-6 sets of friction plates. Power transmission is achieved using these limited friction plates during engagement, which leads to the following drawbacks: First, the small number of friction plates requires high oil pressure to achieve the necessary friction for torque transmission, resulting in significant impact and noticeable jerking during engagement, leading to poor shifting comfort. Second, the limited number of friction plates bearing the burden of high torque transmission and using high oil pressure for engagement causes significant wear and tear over long-term use, leading to deformation, failure, and a high clutch failure rate with a short lifespan. Third, the high oil pressure results in a high load on the high-pressure oil circuit system, making components in the oil circuit, especially seals, more prone to failure. Fourth, in the event of a clutch failure, the entire transmission's input shaft and other components must be disassembled for repair, making maintenance extremely inconvenient. Utility Model Content

[0005] The technical problem to be solved by this utility model is to provide a clutch-biased gearbox and a tractor using the gearbox, which realizes more friction plates in the clutch, which helps to reduce oil pressure and improve torque transmission capability, improve shifting comfort, extend clutch service life and improve maintenance convenience.

[0006] To solve the above-mentioned technical problems, the technical solution of this utility model is: a clutch-biased transmission, including a housing, a transmission assembly installed in the housing, a power input shaft installed on the housing, and a wet clutch assembly installed on the side of the transmission assembly in the housing, with the wet clutch assembly and the transmission assembly arranged in parallel; the power component in the wet clutch assembly is poweredly connected to the power input shaft through a clutch power input mechanism, and the driven component in the wet clutch assembly is poweredly connected to the transmission assembly through a clutch power output mechanism.

[0007] As a preferred technical solution, the wet clutch assembly includes a forward gear clutch assembly and a reverse gear clutch assembly.

[0008] As a preferred technical solution, the clutch power input mechanism includes a forward system input mechanism that is poweredly connected to the power component of the forward gear clutch assembly and a reverse system input mechanism that is poweredly connected to the power component of the reverse gear clutch assembly; the clutch power output mechanism includes a forward system output mechanism that is poweredly connected to the driven component of the forward gear clutch assembly and a reverse system output mechanism that is poweredly connected to the driven component of the reverse gear clutch assembly.

[0009] As a preferred technical solution, the forward gear input mechanism includes a forward gear input drive shaft rotatably mounted in the housing, the forward gear input drive shaft being poweredly connected to the power component of the forward gear clutch assembly, and the forward gear input drive shaft being gear-driven connected to the power input shaft.

[0010] As a preferred technical solution, the forward gear input drive shaft is poweredly connected to the power component of the reverse gear clutch assembly.

[0011] As a preferred technical solution, the forward gear output mechanism includes a forward gear output drive shaft rotatably mounted in the housing, the forward gear output drive shaft being connected to the driven gear of the forward gear clutch assembly, and the forward gear output drive shaft being connected to the gear transmission assembly.

[0012] As a preferred technical solution, the forward gear output drive shaft and the driven component of the reverse gear clutch assembly are connected by a reverse gear idler gear.

[0013] As a preferred technical solution, the wet clutch assembly includes a clutch hub and a center component rotatably mounted in the housing; an annular cavity is formed on the inner side of the clutch hub, and a plurality of alternately arranged outer friction plates and inner friction plates are installed in the annular cavity. The outer friction plates are circumferentially fixed and axially slidably connected to the clutch hub, and the inner friction plates are circumferentially fixed and axially slidably connected to the center component. A clutch control mechanism for pressing or releasing the pressing of the outer friction plates and inner friction plates is provided in the annular cavity.

[0014] As a preferred technical solution, the clutch control mechanism includes a piston, and a clamping and limiting structure is fixedly provided on the clutch hub and / or the center member on the side of the outer friction plate and the inner friction plate away from the piston.

[0015] A tractor using the aforementioned clutch-biased transmission includes a chassis on which the clutch-biased transmission is mounted.

[0016] By adopting the above technical solution, this utility model achieves the following beneficial effects: (1) The wet clutch assembly in the housing is arranged side by side with the transmission assembly, which is free from the space occupied by the gear set and other structures in the transmission assembly. It can achieve a length setting similar to that of the transmission assembly in the length direction, so more friction plates can be configured therein. The configuration of more friction plates is conducive to improving the overall friction force, and can achieve better torque transmission capability when the oil pressure is reduced. (2) More friction plates generate friction more gradually during the pressing process, resulting in smoother engagement and improved shifting comfort; (3) Lower oil pressure can reduce friction plate wear, significantly reduce deformation, thermal failure and other problems, which is conducive to reducing the failure rate and extending the service life of the clutch; lower oil pressure is also conducive to reducing the load on the high-pressure oil circuit and reducing oil circuit failure. (4) The wet clutch assembly is set on the side. When a cover is set at the corresponding position on the housing, it can be installed independently on the cover. Therefore, when the cover is removed, the wet clutch assembly can be disassembled separately, and the transmission assembly no longer needs to be disassembled, which is conducive to improving maintenance convenience. Attached Figure Description

[0017] The following figures are intended only to illustrate and explain the present invention and do not limit the scope of the present invention. Wherein: Figure 1 This is a three-dimensional structural schematic diagram of an embodiment of the present utility model; Figure 2 yes Figure 1 A schematic diagram of the AA structure; Figure 3 yes Figure 2 Enlarged schematic diagram of structure I in the diagram; Figure 4 yes Figure 2 A schematic diagram of the BB structure in the image; Figure 5 yes Figure 2 A schematic diagram of the CC structure in the diagram; Figure 6 yes Figure 2A schematic diagram of the DD structure in the diagram; Figure 7 yes Figure 2 A schematic diagram of the K-axis structure in the diagram; Figure 8 yes Figure 7 A schematic diagram of the EE structure.

[0018] In the diagram: 1-Transmission assembly; 11-First drive shaft; 2-Wet clutch assembly; 21-Clutch hub; 22-Center component; 23-Center shaft; 24-Outer friction plate; 25-Inner friction plate; 26-Clutch control mechanism; 261-Piston; 262-Piston chamber; 263-Pressure limiting structure; 264-Return elastic element; 3-Forward gear clutch assembly; 4-Reverse gear clutch assembly; 5-Clutch power input mechanism; 51-Forward input mechanism; 52-Reverse input mechanism; 53-Forward input drive shaft; 54-Intermediate idler wheel; 6-Clutch power output mechanism; 61-Forward output mechanism; 62-Reverse output mechanism; 63-Forward output drive shaft; 64-Reverse idler wheel; 7-Power input shaft; 9-Box; 91-Cover. Detailed Implementation

[0019] The present invention will be further described below with reference to the accompanying drawings and embodiments. In the following detailed description, only certain exemplary embodiments of the present invention are described by way of illustration. Undoubtedly, those skilled in the art will recognize that various modifications can be made to the described embodiments without departing from the spirit and scope of the present invention. Therefore, the drawings and description are illustrative in nature and not intended to limit the scope of the claims.

[0020] like Figure 7 As shown, the clutch-biased transmission includes a housing 9. The housing 9 represents a well-known and commonly used technology, and its specific structure is not described in detail here or shown in the figure. A transmission assembly 1 is installed inside the housing 9. The transmission assembly 1 is an integral structure with multiple sets of gear transmissions and the ability to switch between these sets to form gear shifting. Its specific structure can be designed using conventional techniques; this embodiment does not limit its specific structure. A power input shaft 7 is installed on the housing 9. The power input shaft 7 is connected to the output end of a power source, inputting drive power to the transmission; specifically, the input is rotational power.

[0021] like Figure 1As shown in the diagram, in this embodiment, a wet clutch assembly 2 is installed on the side of the transmission assembly 1 within the housing 9, and the wet clutch assembly 2 and the transmission assembly 1 are arranged side-by-side. This side-by-side arrangement frees the wet clutch assembly 2 from the space constraints of the gear sets and other structures in the transmission assembly 1. Utilizing the larger space on the side, it can achieve a length similar to the transmission assembly 1, thus allowing for the placement of more friction plates. The increased friction plates improve overall friction, resulting in better torque transmission even with reduced oil pressure.

[0022] The transmission assembly 1 has a structure with at least two shafts, with its upper gear set and other components mounted axially, forming an assembly structure of a certain length. Therefore, its length direction is referenced to the axial direction. Similarly, the wet clutch assembly 2, as a rotating body, has at least one axis, and its length direction is referenced to the axis direction. The above explanations of the two length directions are not intended to limit the scope of protection, but rather to make the structure and effects of this embodiment clearer.

[0023] like Figure 1 As shown, the power component in the wet clutch assembly 2 is poweredly connected to the power input shaft 7 via the clutch power input mechanism 5, and the driven component in the wet clutch assembly 2 is poweredly connected to the transmission assembly 1 via the clutch power output mechanism 6. Thus, the power input from the power input shaft 7 can be transmitted to the transmission assembly 1 via the wet clutch assembly 2; more specifically, when the wet clutch assembly 2 is engaged, power is transmitted to the transmission assembly 1, and when the wet clutch assembly 2 is disengaged, power to the transmission assembly 1 is cut off.

[0024] Normally, such as Figure 2 , Figure 3 and Figure 8As shown, the wet clutch assembly 2 includes a clutch hub 21 and a center component 22 rotatably mounted within the housing 9. An annular cavity is formed on the inner side of the clutch hub 21, and a plurality of alternately arranged outer friction plates 24 and inner friction plates 25 are installed within the annular cavity. The outer friction plates 24 are circumferentially fixed to the clutch hub 21 and axially slidably connected to it. The inner friction plates 25 are circumferentially fixed to the center component 22 and axially slidably connected to it. Both circumferentially fixed and axially slidably connected connections can be achieved using key connections, more preferably using spline connections. A clutch control mechanism 26 for pressing or releasing the outer friction plates 24 and inner friction plates 25 is provided within the annular cavity. After the clutch control mechanism 26 controls the pressing of the outer friction plate 24 and the inner friction plate 25, the friction between the two causes a power transmission between the clutch hub 21 and the center member 22. After the clutch control mechanism 26 controls the release of the pressing of the outer friction plate 24 and the inner friction plate 25, the power transmission between the two is cut off.

[0025] In this embodiment, both the clutch hub 21 and the center component 22 can serve as power components, and when one serves as a power component, the other serves as a driven component. The specific choice between power and driven components can be made according to actual design requirements; this embodiment does not impose such restrictions. This embodiment only describes the structural principle using the clutch hub 21 as the power component and the center component 22 as the driven component. Thus, in this embodiment, the power from the power input shaft 7 is transmitted to the clutch hub 21 through the clutch power input mechanism 5. The clutch hub 21 and the outer friction plate 24 maintain rotation when power is input. After the clutch control mechanism 26 drives and presses the outer friction plate 24 and the inner friction plate 25, the resulting friction force transmits the rotational power to the center component 22. The center component 22 then transmits the power to the transmission assembly 1 through the clutch power output mechanism 6. This embodiment illustrates the center component 22 as a sleeve structure that slides (i.e., is rotatably mounted) on a central shaft 23; however, it is also possible for it to be directly fixed on the central shaft 23.

[0026] like Figure 3As shown, the clutch control mechanism 26 includes a piston 261. In this embodiment, the inner circumferential surface of the piston 261 is in a sealed sliding fit with the central shaft 23, and the outer circumferential surface of the piston 261 is in a sealed sliding fit with the clutch hub 21. A piston cavity 262 is formed between the clutch hub 21 and the central shaft 23 on the side of the piston 261 away from the outer friction plate 24 and the inner friction plate 25. A clamping and limiting structure 263 is fixedly provided on the clutch hub 21 and / or the central member 22 on the side of the outer friction plate 24 and the inner friction plate 25 away from the piston 261. When power engagement is required, high-pressure oil is supplied to the piston chamber 262, driving the piston 261 to move towards the outer friction plate 24 and the inner friction plate 25. Under the constraint of the clamping and limiting structure 263, the outer friction plate 24 and the inner friction plate 25 are ultimately clamped together. When power disengagement is required, the high-pressure oil supply to the piston chamber 262 is canceled or withdrawn, and the piston 261 loses the high-pressure oil pressure drive, releasing the clamping of the outer friction plate 24 and the inner friction plate 25. Conventionally, the piston 261 is connected to a return elastic element 264, so that after the high-pressure oil supply is canceled or withdrawn, the return elastic element 264 can rely on its elastic force to assist the piston 261 in quickly releasing the clamping of the outer friction plate 24 and the inner friction plate 25, achieving rapid power disengagement. The structural principle of the clutch control mechanism 26 described above is easily understood by those skilled in the art based on existing technology, and will not be elaborated further here. Of course, the clutch control mechanism 26 described in this embodiment is not limited to the above structure. For example, the piston 261 is only provided at the piston cavity 262 formed on the clutch hub 21, and it only has a sealing sliding fit with the piston cavity 262 of the clutch hub 21, etc. These structural forms are all within the protection scope of the clutch control mechanism 26.

[0027] Given the need for tractors to move forward and backward, preferably, such as Figure 1 , Figure 2 and Figure 8 As shown, the wet clutch assembly 2 includes a forward gear clutch assembly 3 and a reverse gear clutch assembly 4. Preferably, the forward gear clutch assembly 3 and the reverse gear clutch assembly 4 are arranged sequentially along the axial direction. In this configuration, the central component 22 of the forward gear clutch assembly 3 and the reverse gear clutch assembly 4 in this embodiment can slide on the same central shaft 23. Of course, if the central component 22 is fixedly mounted on the central shaft 23, the corresponding central shafts 23 of the forward gear clutch assembly 3 and the reverse gear clutch assembly 4 should be separate and able to rotate relative to each other.

[0028] Based on the above settings of the forward gear clutch assembly 3 and the reverse gear clutch assembly 4, such as Figure 1 and Figure 2As shown, the clutch power input mechanism 5 in this embodiment includes a forward gear input mechanism 51 powered by the power component of the forward gear clutch assembly 3 and a reverse gear input mechanism 52 powered by the power component of the reverse gear clutch assembly 4. The clutch power output mechanism 6 includes a forward gear output mechanism 61 powered by the driven component of the forward gear clutch assembly 3 and a reverse gear output mechanism 62 powered by the driven component of the reverse gear clutch assembly 4. This enables the engagement and disengagement of the clutch for forward and reverse gear shifting, respectively.

[0029] like Figure 1 and Figure 2 As shown, the forward gear input mechanism 51 in this embodiment includes a forward gear input drive shaft 53 rotatably mounted within the housing 9. The forward gear input drive shaft 53 is power-connected to the power component of the forward gear clutch assembly 3, and is also gear-connected to the power input shaft 7. That is, this embodiment achieves the power connection between the power input shaft 7 and the power component of the forward gear clutch assembly 3 through the transition of the forward gear input drive shaft 53. More specifically, regarding the clutch hub 21 illustrated in this embodiment as the power component, it represents gear transmission between the forward gear input drive shaft 53 and the clutch hub 21 of the forward gear clutch assembly 3. When direct gear transmission between the forward gear input drive shaft 53 and the power input shaft 7 is not possible, gear transmission can be achieved by using intermediate idler gears 54. The number of intermediate idler gears 54 is designed according to the rotation direction of the transmission and the distance between the power input shaft 7 and the forward gear input drive shaft 53, etc. This is something that those skilled in the art can know using conventional technical means, and will not be elaborated further here. In this embodiment, the power input shaft 7 is coaxial with the first drive shaft 11 of the transmission assembly 1, and the power component in the wet clutch assembly 2 rotates in the same direction as the power input shaft 7. Therefore, two intermediate idler pulleys 54 are used. In this case, one of the intermediate idler pulleys 54 is rotatably mounted on the central shaft 23, which can improve the structural compactness. Of course, the power input shaft 7 is not necessarily coaxial with the first drive shaft 11 of the transmission assembly 1. For example, when the power component of the wet clutch assembly 2 needs to rotate in the opposite direction to the power input shaft 7, the forward gear input drive shaft 53 can be directly used as the power input shaft 7. These transformation methods should all be within the protection range of the forward gear input mechanism 51.

[0030] Preferably, such as Figure 1 and Figure 2 As shown, the forward gear input drive shaft 53 is poweredly connected to the power component of the reverse gear clutch assembly 4. Thus, the reverse gear input mechanism 52 and the forward gear input mechanism 51 share the forward gear input drive shaft 53 and its upstream transmission structure, thereby simplifying the structural layout and improving the structural compactness.

[0031] like Figure 1 , Figure 2 as well as Figures 4 to 6 As shown, the forward gear output mechanism 61 includes a forward gear output drive shaft 63 rotatably mounted within the housing 9. The forward gear output drive shaft 63 is gear-driven connected to the driven member of the forward gear clutch assembly 3, and also gear-driven connected to the transmission assembly 1. In this embodiment, the forward gear output drive shaft 63 facilitates the power connection between the driven member of the forward gear clutch assembly 3 and the transmission assembly 1. More specifically, in this embodiment, the central member 22, as the driven member, is gear-driven to the forward gear clutch assembly 3, and the forward gear output drive shaft 63 is gear-driven to the first drive shaft 11 in the transmission assembly 1. Based on this structure, in this embodiment, the forward gear clutch assembly 3 and the first drive shaft 11 of the transmission assembly 1 rotate in the same direction, that is, the first drive shaft 11 rotates in the same direction as the power input shaft 7. Similarly, when the direction of rotation of the first drive shaft 11 is required to be opposite to that of the center member 22, the forward drive output shaft 63 may not be provided, and this measure should also be within the protection range of the forward drive output mechanism 61.

[0032] Preferably, such as Figure 6 As shown, the forward gear output drive shaft 63 and the driven component of the reverse gear clutch assembly 4 are connected by a reverse gear idler wheel 64. Thus, the reverse gear output mechanism 62 and the forward gear output mechanism 61 share the forward gear output drive shaft 63 and its downstream transmission structure, achieving the same goal of improving structural compactness. Furthermore, after the reverse gear clutch assembly 4 is engaged, the direction of rotation of the forward gear output drive shaft 63 can be changed via the reverse gear idler wheel 64, achieving reverse drive transmission from the transmission assembly 1, i.e., reverse transmission. Of course, this embodiment does not necessarily require a reverse idler wheel 64 to be set at the reverse output mechanism 62 to realize the reverse gear. It is also possible to set a reverse gear position separately in the transmission assembly 1. In this case, the driven part of the reverse clutch assembly 4, that is, its center part 22, can be the same as the center part 22 in the forward clutch assembly 3, and directly gear drive the forward output transmission shaft 63. In this case, when the direction of the first transmission shaft 11 needs to be opposite to that of the center part 22, the center parts 22 of the forward clutch assembly 3 and the reverse clutch assembly 4 can be directly gear driven with the first transmission shaft 11 of the transmission assembly 1. These transformation methods are also within the protection scope of the utility model.

[0033] This embodiment also provides a tractor using the aforementioned clutch-biased transmission, including a chassis on which the clutch-biased transmission is mounted.

[0034] In this embodiment, the wet clutch assembly 2 is arranged side-by-side with the transmission assembly 1, allowing for a greater number of friction plates, which helps reduce oil pressure and improve torque transmission capability. With more friction plates, the friction force is generated more gradually during the pressing process, resulting in smoother engagement and improved shifting comfort. Lower oil pressure reduces friction plate wear, significantly reducing deformation and thermal failure, thus lowering the failure rate and extending clutch life. Lower oil pressure also helps reduce the load on the high-pressure oil circuit, reducing oil circuit failures. With the wet clutch assembly 2 arranged side-by-side, and a cover 91 corresponding to the position on the housing 9, as... Figure 7 As shown, it can be installed independently on the cover 91, so when the cover 91 is removed, the wet clutch assembly 2 can be disassembled separately, and it is no longer necessary to disassemble the transmission assembly 1, which helps to improve maintenance convenience.

[0035] The foregoing has shown and described the basic principles, main features, and advantages of this utility model. Those skilled in the art should understand that this utility model is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of this utility model. Various changes and modifications can be made to this utility model without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claims. The scope of protection of this utility model is defined by the appended claims and their equivalents.

Claims

1. A clutch-biased transmission, comprising a housing, wherein a transmission assembly is mounted within the housing, and a power input shaft is mounted on the housing, characterized in that: A wet clutch assembly is installed on the side of the transmission assembly inside the housing, and the wet clutch assembly and the transmission assembly are arranged in parallel. The power component in the wet clutch assembly is poweredly connected to the power input shaft through a clutch power input mechanism, and the driven component in the wet clutch assembly is poweredly connected to the transmission assembly through a clutch power output mechanism.

2. The clutch-biased transmission as described in claim 1, characterized in that: The wet clutch assembly includes a forward gear clutch assembly and a reverse gear clutch assembly.

3. The clutch-biased transmission as described in claim 2, characterized in that: The clutch power input mechanism includes a forward gear input mechanism that is poweredly connected to the power component of the forward gear clutch assembly and a reverse gear input mechanism that is poweredly connected to the power component of the reverse gear clutch assembly. The clutch power output mechanism includes a forward gear output mechanism that is poweredly connected to the driven component of the forward gear clutch assembly and a reverse gear output mechanism that is poweredly connected to the driven component of the reverse gear clutch assembly.

4. The clutch-biased transmission as described in claim 3, characterized in that: The forward gear input mechanism includes a forward gear input drive shaft rotatably mounted inside the housing. The forward gear input drive shaft is poweredly connected to the power component of the forward gear clutch assembly, and the forward gear input drive shaft is gear-driven connected to the power input shaft.

5. The clutch-biased transmission as described in claim 4, characterized in that: The forward gear input drive shaft is poweredly connected to the power component of the reverse gear clutch assembly.

6. The clutch-biased transmission as described in claim 3, characterized in that: The forward gear output mechanism includes a forward gear output drive shaft rotatably mounted inside the housing. The forward gear output drive shaft is connected to the driven gear of the forward gear clutch assembly, and the forward gear output drive shaft is connected to the gear of the transmission assembly.

7. The clutch-biased transmission as described in claim 6, characterized in that: The forward drive shaft and the driven component of the reverse clutch assembly are connected by a reverse idler gear.

8. The clutch-biased transmission as described in claim 1, characterized in that: The wet clutch assembly includes a clutch hub and a center component rotatably mounted in the housing; an annular cavity is formed on the inner side of the clutch hub, and a plurality of alternately arranged outer friction plates and inner friction plates are installed in the annular cavity. The outer friction plates are circumferentially fixed and axially slidably connected to the clutch hub, and the inner friction plates are circumferentially fixed and axially slidably connected to the center component. A clutch control mechanism for pressing or releasing the pressing of the outer friction plates and inner friction plates is provided in the annular cavity.

9. The clutch-biased transmission as described in claim 8, characterized in that: The clutch control mechanism includes a piston, and a clamping and limiting structure is fixedly provided on the clutch hub and / or the center member on the side of the outer friction plate and the inner friction plate away from the piston.

10. A tractor using a clutch-biased gearbox as described in any one of claims 1 to 9, comprising a chassis, characterized in that: The clutch-biased transmission is mounted on the chassis.

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