A forage cutter feeding transmission gearbox, transmission system and forage cutter

Abstract

This utility model relates to a cutting and feeding transmission gearbox, transmission system, and silage harvester, belonging to the field of agricultural machinery. In the cutting and feeding transmission gearbox, both the intermediate gear shaft and the conveying shaft are rotatably mounted within the housing. An overrunning clutch mechanism is mounted on the intermediate gear shaft and is connected to the driven gear shaft of the cutter head. The overrunning clutch mechanism is used to transmit power unidirectionally from the intermediate gear shaft to the driven gear shaft of the cutter head. The driven gear shaft of the cutter head is rotatably mounted on the conveying shaft, and the intermediate gear shaft is connected to the conveying shaft. The beneficial effects of this utility model are: it realizes the coexistence of silage cutting and conveying functions, greatly improving the operating efficiency of the silage harvester; the internal structure of the gearbox is compact, reducing the gearbox volume; after the intermediate gear shaft stops rotating, the transmission between the intermediate gear shaft and the driven gear shaft of the cutter head disengages, avoiding damage to the intermediate gear shaft caused by the cutter head continuing to rotate due to inertia.

Description

Technical Field

[0001] This utility model relates to the field of agricultural machinery, specifically to a cutting and feeding transmission gearbox, transmission system, and silage harvester. Background Technology

[0002] As the market demands higher standards for silage harvesting machinery, users are also placing greater emphasis on the operational efficiency of silage harvesters. Existing cutting and feeding transmission gearboxes employ two independent transmission structures to achieve the cutting and conveying functions of silage, resulting in low transmission efficiency and a large footprint. Furthermore, when the machine is stopped, the cutting disc continues to rotate due to inertia, which can easily damage the internal structure of the gearbox. Utility Model Content

[0003] The technical problem to be solved by this utility model is how to provide a high-efficiency and compact forage cutter feeding transmission gearbox.

[0004] The technical solution of this utility model to solve the above-mentioned technical problems is as follows: A cutting and feeding transmission gearbox for a silage harvester includes a housing, an intermediate gear shaft, an overrunning clutch mechanism, a conveying shaft, and a cutter head driven gear shaft. The intermediate gear shaft and the conveying shaft are both rotatably mounted in the housing. The overrunning clutch mechanism is mounted on the intermediate gear shaft and is drivenly connected to the cutter head driven gear shaft. The overrunning clutch mechanism is used to transmit power unidirectionally from the intermediate gear shaft to the cutter head driven gear shaft. The cutter head driven gear shaft is rotatably sleeved on the conveying shaft, and the intermediate gear shaft is drivenly connected to the conveying shaft.

[0005] The beneficial effects of this utility model are: the intermediate gear shaft is used to transmit the input power to the cutter head driven gear shaft through the overrunning clutch mechanism, and the cutter head driven gear shaft drives the cutter head to rotate to achieve cutting; at the same time, the intermediate gear shaft also transmits power to the conveying shaft, and the conveying shaft is used to drive the conveying mechanism to achieve the conveying of silage, and the power is effectively differentiated inside the gear box.

[0006] 1. The cutting and feeding transmission gearbox of the silage machine realizes the coexistence of silage cutting and conveying functions, which greatly improves the operating efficiency of the silage machine. The internal structure of the gearbox is compact, reducing the size of the gearbox.

[0007] 2. The forage cutter's feed transmission gearbox is equipped with an overrunning clutch mechanism, which enables unidirectional power transmission and reverse disengagement. After the intermediate gear shaft stops rotating, the transmission between the intermediate gear shaft and the cutter head's driven gear shaft is disengaged, preventing damage to the intermediate gear shaft caused by the cutter head continuing to rotate due to inertia.

[0008] Based on the above technical solution, the present invention can be further improved as follows.

[0009] Furthermore, the overrunning clutch mechanism includes a clutch tray, a cutter head drive gear, and a spring assembly. The clutch tray is splinedly connected to the intermediate gear shaft. The clutch tray includes a coaxially fixed cylinder and a disc body. The cutter head drive gear is rotatably sleeved on the outside of the cylinder. The disc body has a clutch groove on one end face facing the cutter head drive gear. One end of the spring assembly abuts against the clutch groove, and the other end abuts against or is fixedly connected to the cutter head drive gear. The clutch groove is an arc-shaped groove opened along the circumference of the disc body. The depth of the clutch groove gradually increases from one end to the other along its circumference. The cutter head drive gear is shaft-driven connected to the cutter head driven gear.

[0010] The beneficial effects of adopting the above-mentioned further solution are as follows: When the intermediate gear shaft rotates, it drives the clutch tray to rotate synchronously. At this time, the spring assembly is stuck at the end with the greater depth of the clutch groove, synchronously driving the cutter head drive gear to rotate, transmitting power to the cutter head driven gear shaft. When the intermediate gear shaft stops rotating, due to the inertia of the cutter head, it will continue to rotate for a period of time. The cutter head driven gear shaft, the cutter head drive gear, and the spring assembly will still rotate in the original direction under the action of inertia. The clutch tray and the cutter head drive gear will generate relative rotation. The spring assembly slides from the deeper end of the clutch groove to the shallower end. After sliding out of the clutch groove, with the relative rotation of the clutch tray and the cutter head drive gear, it slides back into the deeper end of the clutch groove, thereby disengaging the power transmission between the clutch tray and the cutter head drive gear. Finally, the cutter head stops rotating under the action of resistance and friction. At the same time, when the clutch tray and the cutter head drive gear rotate relative to each other, due to the arc-shaped slide structure of the clutch groove, the degree of compression of the spring assembly by the clutch groove changes accordingly, and the spring force also changes. This causes the stopping force acting on the cutter head drive gear (the friction between the spring assembly and the clutch tray and the spring force of the spring assembly) to exhibit a reciprocating state from small to large, which can make the cutter head drive gear stop rotating quickly and smoothly.

[0011] Furthermore, the spring assembly includes a spring and a spring seat. One end of the spring seat abuts against the clutch groove, and the other end has a limiting hole. The end face of the cutter head drive gear facing the disc body has a spring mounting groove. One end of the spring abuts against the spring mounting groove, and the other end abuts against the limiting hole.

[0012] The advantages of adopting the above-mentioned further solution are: the spring applies an elastic force to the spring seat so that it abuts against the clutch tray, the spring seat abuts against and slides with the clutch groove, the spring seat can be replaced after wear, avoiding the need for complete replacement beyond the clutch mechanism, and reducing maintenance costs.

[0013] Furthermore, the disc body is provided with a plurality of clutch grooves spaced apart along its circumference.

[0014] Furthermore, an intermediate gear is integrally formed on the intermediate gear shaft, and a conveying driven gear is fixed on the conveying shaft. The intermediate gear meshes with the conveying driven gear for transmission.

[0015] The beneficial effect of adopting the above-mentioned further solution is that the intermediate gear shaft transmits power to the conveyor shaft through the intermediate gear and the conveyor driven gear.

[0016] Furthermore, both the intermediate gear and the driven conveying gear are helical gears.

[0017] The beneficial effects of adopting the above-mentioned further scheme are: the helical gear transmission is smooth, with less impact, vibration and noise, and is suitable for high-speed and heavy-load transmission scenarios. Therefore, the power of silage transportation is transmitted by helical gears.

[0018] Furthermore, the forage cutter feeding transmission gearbox also includes a power input bevel gear shaft, which is rotatably mounted inside the housing and is connected to the intermediate gear shaft for transmission.

[0019] The beneficial effect of adopting the above-mentioned further scheme is that the power input bevel gear shaft is used to input power and transmit the power to the intermediate gear shaft.

[0020] Furthermore, an input bevel gear is integrally formed on the power input bevel gear shaft, and a driven bevel gear is fixed on the intermediate gear shaft. The input bevel gear and the driven bevel gear mesh and transmit power.

[0021] This utility model also provides a transmission system, including a cutter head, a conveying mechanism, and the cutting and feeding transmission gearbox of the silage harvester, wherein the cutter head is drivenly connected to the cutter head driven gear shaft, and the conveying mechanism is drivenly connected to the conveying shaft.

[0022] The beneficial effects are: the cutting and feeding transmission gearbox of the silage harvester simultaneously drives the cutter head and conveying mechanism, improving transmission efficiency. Furthermore, the gearbox is equipped with an overrunning clutch mechanism, enabling unidirectional transmission with the cutter head, thus preventing damage to the intermediate gear shaft caused by the cutter head continuing to rotate due to inertia after the intermediate gear shaft has stopped.

[0023] This utility model also provides a silage machine, including the silage machine cutting and feeding transmission gearbox. Attached Figure Description

[0024] Figure 1 This is a front view of the cutting and feeding transmission gearbox of a silage harvester according to this utility model;

[0025] Figure 2 This is a left view of the cutting and feeding transmission gearbox of a silage harvester according to the present invention;

[0026] Figure 3This is an axial view of the clutch tray of this utility model;

[0027] Figure 4 for Figure 3 BB section view of clutch tray.

[0028] It should be noted that, Figure 1 and Figure 2 The housing is not shown.

[0029] The attached diagram lists the components represented by each number as follows:

[0030] 1. Power input bevel gear shaft; 2. Driven bevel gear; 3. Intermediate gear shaft; 4. Clutch tray; 41. Clutch groove; 5. Cutter head drive gear; 6. Spring seat; 7. Conveyor driven gear; 8. Conveyor shaft; 9. Cutter head driven gear shaft. Detailed Implementation

[0031] The principles and features of this utility model are described below with reference to the accompanying drawings. The examples given are only for explaining this utility model and are not intended to limit the scope of this utility model.

[0032] Example 1

[0033] like Figures 1-4 As shown, this embodiment provides a cutting and feeding transmission gearbox for a silage harvester, including a housing, an intermediate gear shaft 3, an overrunning clutch mechanism, a conveying shaft 8, and a cutter head driven gear shaft 9. The intermediate gear shaft 3 and the conveying shaft 8 are both rotatably mounted in the housing. The overrunning clutch mechanism is mounted on the intermediate gear shaft 3 and is drive-connected to the cutter head driven gear shaft 9. The overrunning clutch mechanism is used to transmit power unidirectionally from the intermediate gear shaft 3 to the cutter head driven gear shaft 9. The cutter head driven gear shaft 9 is rotatably sleeved on the conveying shaft 8, and the intermediate gear shaft 3 is drive-connected to the conveying shaft 8.

[0034] In this embodiment, the intermediate gear shaft 3 is used to transmit the input power to the cutter head driven gear shaft 9 through the overrunning clutch mechanism. The cutter head driven gear shaft 9 drives the cutter head to rotate to achieve cutting. At the same time, the intermediate gear shaft 3 also transmits power to the conveying shaft 8. The conveying shaft 8 is used to drive the conveying mechanism to achieve the conveying of silage, and achieves effective power differentiation inside the gear box.

[0035] 1. The cutting and feeding transmission gearbox of the silage machine realizes the coexistence of silage cutting and conveying functions, which greatly improves the operating efficiency of the silage machine. The internal structure of the gearbox is compact, reducing the size of the gearbox.

[0036] 2. The cutting and feeding transmission gearbox of the silage cutter is equipped with an overrunning clutch mechanism to realize the function of unidirectional power transmission and reverse disengagement. After the intermediate gear shaft 3 stops rotating, the transmission between the intermediate gear shaft 3 and the cutter head driven gear shaft 9 is disengaged, which avoids damage to the intermediate gear shaft 3 caused by the cutter head continuing to rotate due to inertia.

[0037] Specifically, the intermediate gear shaft 3 and the conveying shaft 8 are both rotatably mounted on the housing via bearings, and the cutter head driven gear shaft 9 is rotatably sleeved on the conveying shaft 8 via bearings.

[0038] Specifically, one end of the conveyor shaft 8 extends out of the housing and has a spline for transmission connection with the conveying mechanism. One end of the cutter head driven gear shaft 9 extends out of the housing and is used for connection with the cutter head.

[0039] Based on the above technical solution, the overrunning clutch mechanism can be an existing overrunning clutch; or, the overrunning clutch mechanism includes a clutch tray 4, a cutter head drive gear 5, and a spring assembly. The clutch tray 4 is splinedly connected to the intermediate gear shaft 3. The clutch tray 4 includes a coaxially fixed cylinder and a disc body. The cutter head drive gear 5 is rotatably sleeved on the outside of the cylinder. The disc body has a clutch groove 41 on one end face facing the cutter head drive gear 5. One end of the spring assembly abuts against the clutch groove 41, and the other end abuts against or is fixedly connected to the cutter head drive gear 5. The clutch groove 41 is an arc-shaped groove opened along the circumference of the disc body. The depth of the clutch groove 41 gradually increases from one end to the other in the circumferential direction. The cutter head drive gear 5 is drively connected to the cutter head driven gear shaft 9.

[0040] When the intermediate gear shaft 3 rotates, it drives the clutch tray 4 to rotate synchronously. At this time, the spring assembly is engaged at the deeper end of the clutch groove 41, synchronously driving the cutter head drive gear 5 to rotate, transmitting power to the cutter head driven gear shaft 9. When the intermediate gear shaft 3 stops rotating, due to the inertia of the cutter head, it will continue to rotate for a period of time. The cutter head driven gear shaft 9, the cutter head drive gear 5, and the spring assembly will still rotate in the original direction under the action of inertia. The clutch tray 4 and the cutter head drive gear 5 will generate relative rotation. The spring assembly slides from the deeper end of the clutch groove 41 to the shallower end. After sliding out of the clutch groove 41, with the relative rotation of the clutch tray 4 and the cutter head drive gear 5, it slides back into the deeper end of the clutch groove 41, thereby disengaging the power transmission between the clutch tray 4 and the cutter head drive gear 5. Finally, the cutter head stops rotating under the action of resistance and friction. At the same time, when the clutch tray and the cutter head drive gear rotate relative to each other, due to the arc-shaped slide structure of the clutch groove, the degree of compression of the spring assembly by the clutch groove changes accordingly, and the spring force also changes. This causes the stopping force acting on the cutter head drive gear (the friction between the spring assembly and the clutch tray and the spring force of the spring assembly) to exhibit a reciprocating state from small to large, which can make the cutter head drive gear stop rotating quickly and smoothly.

[0041] Specifically, the cutter head driven gear is integrally formed or fixedly connected to the cutter head driven gear shaft 9, and the cutter head driving gear 5 meshes with the cutter head driven gear for transmission.

[0042] Based on the above technical solution, the spring assembly includes a spring and a spring seat 6. One end of the spring seat 6 abuts against the clutch groove 41, and the other end has a limiting hole. The end face of the cutter head drive gear 5 facing the disc body has a spring mounting groove. One end of the spring abuts against the spring mounting groove, and the other end abuts against the limiting hole.

[0043] The spring applies an elastic force to the spring seat 6, causing it to abut against the clutch tray 4. The spring seat 6 abuts against and slides with the clutch groove 41. The spring seat 6 can be replaced after wear, avoiding the need for complete replacement beyond the clutch mechanism and reducing maintenance costs.

[0044] Specifically, spring seat 6 is cylindrical, such as... Figure 3 and Figure 4 As shown, the end of the clutch groove 41 is arc-shaped. Alternatively, the spring seat 6 can also be prismatic.

[0045] Based on the above technical solution, the disc body is provided with a plurality of clutch grooves 41 at intervals along its circumference.

[0046] Optionally, there may be one or more spring assemblies, and the number of spring mounting slots shall be the same as the number of spring assemblies, and they shall be set one-to-one.

[0047] Based on the above technical solution, an intermediate gear is integrally formed on the intermediate gear shaft 3, and a conveying driven gear 7 is fixed on the conveying shaft 8. The intermediate gear meshes with the conveying driven gear 7 for transmission.

[0048] The intermediate gear shaft 3 transmits power to the conveyor shaft 8 through the intermediate gear and the conveyor driven gear 7.

[0049] Based on the above technical solution, both the intermediate gear and the conveying passive gear 7 are helical gears.

[0050] Helical gear transmission is smooth with less impact, vibration and noise, making it suitable for high-speed and heavy-load transmission scenarios. Therefore, helical gears are used to transmit power for transporting silage.

[0051] Based on the above technical solution, the cutting and feeding transmission gearbox of the silage machine also includes a power input bevel gear shaft 1, which is rotatably installed in the housing and is connected to the intermediate gear shaft 3 in a transmission manner.

[0052] The power input bevel gear shaft 1 is used to input power and transmit the power to the intermediate gear shaft 3.

[0053] Specifically, the power input bevel gear shaft 1 is rotatably mounted in the housing via bearings.

[0054] Based on the above technical solution, an input bevel gear is integrally formed on the power input bevel gear shaft 1, and a passive bevel gear 2 is fixed on the intermediate gear shaft 3. The input bevel gear and the passive bevel gear 2 mesh and transmit power.

[0055] Example 2

[0056] This embodiment also provides a transmission system, including a cutter head, a conveying mechanism, and the forage machine cutting and feeding transmission gearbox. The cutter head is connected to the cutter head driven gear shaft 9, and the conveying mechanism is connected to the conveying shaft 8.

[0057] In this embodiment, the silage cutter feed transmission gearbox simultaneously drives the cutter head and conveying mechanism, improving transmission efficiency. Furthermore, the gearbox is equipped with an overrunning clutch mechanism, enabling unidirectional transmission with the cutter head, thus preventing damage to the intermediate gear shaft 3 caused by the cutter head continuing to rotate due to inertia after the intermediate gear shaft 3 has stopped.

[0058] Example 3

[0059] This embodiment also provides a silage machine, including the silage machine cutting and feeding transmission gearbox.

[0060] In the description of this utility model, it should be noted that the terms "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0061] In the description of this utility model, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0062] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0063] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0064] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A cutting and feeding transmission gearbox for a silage harvester, characterized in that, The device includes a housing, an intermediate gear shaft (3), an overrunning clutch mechanism, a conveying shaft (8), and a cutter head driven gear shaft (9). The intermediate gear shaft (3) and the conveying shaft (8) are rotatably mounted inside the housing. The overrunning clutch mechanism is mounted on the intermediate gear shaft (3) and is drive-connected to the cutter head driven gear shaft (9). The overrunning clutch mechanism is used to transmit power unidirectionally from the intermediate gear shaft (3) to the cutter head driven gear shaft (9). The cutter head driven gear shaft (9) is rotatably sleeved on the conveying shaft (8). The intermediate gear shaft (3) and the conveying shaft (8) are drive-connected.

2. The forage cutter feeding transmission gearbox according to claim 1, characterized in that, The overrunning clutch mechanism includes a clutch tray (4), a cutter head drive gear (5), and a spring assembly. The clutch tray (4) is splinedly connected to the intermediate gear shaft (3). The clutch tray (4) includes a coaxially fixed cylinder and a disc body. The cutter head drive gear (5) is rotatably sleeved on the outside of the cylinder. The disc body has a clutch groove (41) on one end face facing the cutter head drive gear (5). One end of the spring assembly abuts against the clutch groove (41), and the other end abuts against or is fixedly connected to the cutter head drive gear (5). The clutch groove (41) is an arc-shaped groove opened along the circumference of the disc body. The depth of the clutch groove (41) gradually increases from one end to the other in the circumference. The cutter head drive gear (5) is drivenly connected to the cutter head driven gear shaft (9).

3. The forage machine cutting and feeding transmission gearbox according to claim 2, characterized in that, The spring assembly includes a spring and a spring seat (6). One end of the spring seat (6) abuts against the clutch groove (41), and the other end has a limiting hole. The cutter head drive gear (5) has a spring mounting groove on the end face facing the disc body. One end of the spring abuts against the spring mounting groove, and the other end abuts against the limiting hole.

4. The forage cutter feeding transmission gearbox according to claim 2, characterized in that, The disc body is provided with a plurality of clutch grooves (41) spaced apart along its circumference.

5. The forage machine cutting and feeding transmission gearbox according to claim 1, characterized in that, An intermediate gear is integrally formed on the intermediate gear shaft (3), and a conveying driven gear (7) is fixed on the conveying shaft (8). The intermediate gear meshes with the conveying driven gear (7) for transmission.

6. The forage cutter feeding transmission gearbox according to claim 5, characterized in that, Both the intermediate gear and the conveying driven gear (7) are helical gears.

7. A forage cutter feeding transmission gearbox according to any one of claims 1-6, characterized in that, It also includes a power input bevel gear shaft (1), which is rotatably mounted in the housing and is connected to the intermediate gear shaft (3) in a transmission connection.

8. The forage machine cutting and feeding transmission gearbox according to claim 7, characterized in that, An input bevel gear is integrally formed on the power input bevel gear shaft (1), and a passive bevel gear (2) is fixed on the intermediate gear shaft (3). The input bevel gear meshes with the passive bevel gear (2) for transmission.

9. A transmission system, characterized in that, It includes a cutter head, a conveying mechanism, and a forage cutter feeding transmission gearbox as described in any one of claims 1-8, wherein the cutter head is drivenly connected to the cutter head driven gear shaft (9), and the conveying mechanism is drivenly connected to the conveying shaft (8).

10. A silage harvester, characterized in that, Includes the forage cutter feed transmission gearbox as described in any one of claims 1-8.

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