Vibration reduction type planetary wobble box, header and harvester

Abstract

The utility model discloses a vibration damping type planet wobble ring box, header and harvester, vibration damping type planet wobble ring box comprises a box body, a power input shaft, a planet wheel support and a crank shaft, one end of the power input shaft and one end of the planet wheel support both penetrate into the box body and are both connected with the box body in a rotating mode. The power input shaft is in transmission connection with the end, located in the box body, of the planet wheel support, the planet wheel support is provided with an installation channel, one end of the crank shaft is located in the installation channel and rotationally connected with the planet wheel support, the other end of the crank shaft is located outside the box body, the crank shaft is provided with a planet wheel, and an inner gear ring meshed with the planet wheel is arranged in the box body. Balancing weights are arranged on the edges of the ends, located outside the box body, of the crank shaft and the planet wheel support, so that when the crank shaft and the planet wheel support rotate relatively, lateral excitation can be counteracted through cooperation of the two balancing weights, and the whole vibration reduction type planet wobble ring box is good in stability during operation.

Description

Technical Field

[0001] This utility model belongs to the field of harvester technology, and in particular relates to a vibration-damping planetary swing ring box, header and harvester. Background Technology

[0002] Existing eccentric shaft type planetary pendulum ring boxes also generate a certain amount of lateral motion when driving the cutter in reciprocating motion. This exacerbates the vibration of the cutting table, which leads to increased noise during operation and is prone to failure, reducing the reliability of the equipment. For example, documents CN117515113A "A Novel Planetary Gear Pendulum Ring Box" and CN202790341U "Cutter Drive Device" both disclose a planetary pendulum ring box, but neither of them has vibration reduction capabilities. Utility Model Content

[0003] To solve the above-mentioned technical problems, one of the objectives of this utility model is to provide a vibration-damping planetary ring box with a simple structure and vibration-damping function.

[0004] To achieve the above objectives, the technical solution of this utility model is as follows: A vibration-damping planetary pendulum ring box includes a box body, a power input shaft, a planetary gear support, and a crankshaft. One end of both the power input shaft and the planetary gear support is inserted into the box body and rotatably connected to it. The ends of the power input shaft and the planetary gear support located inside the box body are connected in a transmission manner. The planetary gear support has an installation channel. One end of the crankshaft is located within the installation channel and rotatably connected to the planetary gear support. The other end of the crankshaft is located outside the box body. Planetary gears are mounted on the crankshaft. An internal gear ring meshing with the planetary gears is mounted inside the box body. A first counterweight is located at the edge of the crankshaft located outside the box body, and a second counterweight is located at the edge of the planetary gear support located outside the box body.

[0005] The beneficial effects of this invention are as follows: the power input shaft drives the planetary gear carrier to rotate, while the crankshaft revolves with the planetary gear carrier. At the same time, the crankshaft rotates on its own axis under the combined action of the internal gear ring and the planetary gears. Ultimately, the crankshaft rotates relative to the planetary gear carrier while revolving, and the crankshaft drives the cutting table to run. A first counterweight is set on the crankshaft, and a second counterweight is set on the planetary gear carrier. This allows the crankshaft and the planetary gear carrier to counteract lateral excitation when they rotate relative to each other, thus making the entire vibration-damping planetary pendulum ring box have good stability during operation.

[0006] Based on the above solution, the vibration-damping planetary pendulum ring box of this utility model can be further improved as follows:

[0007] Furthermore, the axis of the mounting channel is parallel to and spaced apart from the axis of the planetary gear support, and the center of gravity of the planetary gear support is far away from the mounting channel.

[0008] The beneficial effect of adopting the above-mentioned further solution is that it allows the center of gravity of the planetary gear support to be further offset from the crankshaft, thereby further improving the vibration reduction effect of the entire vibration-damping planetary ring box.

[0009] Furthermore, the power input shaft is perpendicular to the planetary gear support, and a first bevel gear is coaxially and fixedly mounted on one end of the power input shaft located inside the housing, and a second bevel gear is coaxially and fixedly mounted on one end of the planetary gear support located inside the housing. The first bevel gear and the second bevel gear mesh with each other.

[0010] The beneficial effects of adopting the above-mentioned further scheme are that it enables the entire vibration-damping planetary pendulum box to achieve vertical reversal in power transmission, and its structure is more compact.

[0011] Furthermore, the second counterweight is located on the side of the planetary gear bracket away from the mounting channel at the corresponding end.

[0012] The beneficial effect of adopting the above-mentioned further solution is that it further deviates the center of gravity of the entire planetary gear support from the installation channel, thereby further improving the vibration reduction effect of the entire vibration-damping planetary pendulum box.

[0013] Furthermore, the crankshaft includes a shaft body and a rocker arm. The rocker arm is disposed at one end of the shaft body, and the axis of the rocker arm is parallel to and spaced apart from the axis of the shaft body. The shaft body extends into the mounting channel and is rotatably connected to the planetary gear support. The planetary gears are coaxially and fixedly disposed on the shaft body. The rocker arm is located outside the housing as a power output end.

[0014] The beneficial effect of adopting the above-mentioned further solution is that it creates a gap between the axis of the swing arm and the axis of the shaft, thereby amplifying the amplitude of the cutting blade during reciprocating motion.

[0015] Furthermore, the first counterweight is disposed at one end of the shaft located outside the housing, and the first counterweight is located on the side of the shaft opposite to the swing arm.

[0016] The beneficial effect of adopting the above-mentioned further solution is that it causes the center of gravity of the crankshaft to deviate from the rocker arm, which reduces the lateral excitation of the crankshaft when driving the cutting table.

[0017] Furthermore, the planetary gear bracket has a notch on the side near the mounting channel that communicates with the interior of the mounting channel, and the planetary gear is located within the notch.

[0018] The beneficial effect of adopting the above-mentioned further solution is that the first and second counterweights will not interfere with each other when the crankshaft and planetary gear support are rotating.

[0019] Furthermore, the planetary gear bracket has a notch on the side near the mounting channel that communicates with the interior of the mounting channel, and the planetary gear is located within the notch.

[0020] The beneficial effect of adopting the above-mentioned further solution is that it makes the crankshaft more evenly stressed and less prone to bending and deformation.

[0021] The second objective of this invention is to provide a cutting table with good operational stability.

[0022] To achieve the above objectives, the technical solution of this utility model is as follows: a cutting table, including the vibration-damping planetary pendulum ring box as described above.

[0023] The third objective of this utility model is to provide a harvester with good stability during operation of the header.

[0024] To achieve the above objectives, the technical solution of this utility model is as follows: a harvester, including the cutting platform as described above. Attached Figure Description

[0025] Figure 1 This is a side view of the vibration-damping planetary pendulum ring box described in Embodiment 1 of this utility model;

[0026] Figure 2 This is a cross-sectional view of the vibration-damping planetary pendulum ring box described in Embodiment 1 of this utility model;

[0027] Figure 3 This is an elevation view of a planetary gear support in the prior art;

[0028] Figure 4 This is an elevation view of the planetary gear support described in Embodiment 1 of this utility model;

[0029] Figure 5 This is a schematic diagram of the end face of the planetary gear support near the power input shaft in Embodiment 1 of this utility model;

[0030] Figure 6 This is a cross-sectional view of the planetary gear support described in Embodiment 1 of this utility model;

[0031] Figure 7 This is an elevation view of the crankshaft described in Embodiment 1 of this utility model;

[0032] Figure 8 This is a side view of the crankshaft described in Embodiment 1 of this utility model;

[0033] Figure 9 This is a schematic diagram showing the relative angle of the second counterweight rotating counterclockwise and the first counterweight rotating clockwise when the second counterweight rotates counterclockwise in Embodiment 1 of this utility model.

[0034] Figure 10 This is a schematic diagram showing the relative angle of the second counterweight rotating counterclockwise and the first counterweight rotating clockwise when they rotate in Embodiment 1 of this utility model.

[0035] Figure 11 This is a schematic diagram showing the relative angle of the second counterweight rotating counterclockwise and the first counterweight rotating clockwise when they rotate in Embodiment 1 of this utility model.

[0036] Figure 12 This is a schematic diagram showing the relative angle of the second counterweight rotating counterclockwise and the first counterweight rotating clockwise when they rotate in Embodiment 1 of this utility model.

[0037] Figure 13 This is a schematic diagram showing the relative angle of the second counterweight rotating counterclockwise and the first counterweight rotating clockwise when they rotate in Embodiment 1 of this utility model.

[0038] Figure 14 This is a schematic diagram showing the relative angle of the second counterweight rotating counterclockwise and the first counterweight rotating clockwise when they rotate in Embodiment 1 of this utility model.

[0039] Figure 15 This is a schematic diagram showing the relative angle of the second counterweight rotating counterclockwise and the first counterweight rotating clockwise when they rotate in Embodiment 1 of this utility model.

[0040] Figure 16 This is a schematic diagram showing the relative angle of the second counterweight rotating counterclockwise and the first counterweight rotating clockwise when they rotate in Embodiment 1 of this utility model.

[0041] Figure 17 This is a schematic diagram showing the relative angle of the second counterweight rotating counterclockwise and the first counterweight rotating clockwise when they rotate in Embodiment 1 of this utility model.

[0042] In the diagram: 1. Housing; 2. Power input shaft; 21. Pulley; 3. Planetary gear support; 31. Mounting channel; 32. Notch; 33. Block; 4. Crankshaft; 41. Shaft; 42. Swing arm; 5. Planetary gear; 6. Internal gear ring; 7. First counterweight; 8. Second counterweight; 9. First bevel gear; 10. Second bevel gear. Detailed Implementation

[0043] The principles and features of this utility model are described below with reference to the accompanying drawings. The examples given are for illustrative purposes only and are not intended to limit the scope of this utility model. The utility model is described more specifically in the following paragraphs by way of example with reference to the accompanying drawings. The advantages and features of this utility model will become clearer from the following description and claims. It should be noted that the drawings are all in a very simplified form and use non-precise proportions, and are only used to facilitate and clarify the illustration of the embodiments of this utility model.

[0044] Example 1

[0045] like Figure 1 and Figure 2 As shown, this embodiment provides a vibration-damping planetary pendulum ring housing, which includes a housing 1, a power input shaft 2, a planetary gear carrier 3, and a crankshaft 4. Both the power input shaft 2 and the planetary gear carrier 3 have one end inserted into the housing 1 and are rotatably connected to it. The ends of the power input shaft 2 and the planetary gear carrier 3 located inside the housing 1 are connected in a transmission manner. The planetary gear carrier 3 has mounting channels 31, the axis of which is parallel to and spaced apart from the axis of the planetary gear carrier 3. One end of the crankshaft 4 is located inside the mounting channel 31 and is rotatably connected to the planetary gear carrier 3. The other end of the crankshaft 4 is located outside the housing 1. Planetary gears 5 are mounted on the crankshaft 4. An internal gear ring 6 meshing with the planetary gears 5 is provided inside the housing 1. The crankshaft 4 and the planetary gear carrier 3 are located at the edge of the outer end of the housing 1. Each component is equipped with a counterweight [a first counterweight 7 is provided at the edge of the outer end of the crankshaft 4 located at the outer end of the housing 1 (the outer end of the crankshaft serves as the power output end), and a second counterweight 8 is provided at the edge of the outer end of the planetary gear carrier 3 located at the outer end of the housing 1]; this causes the power input shaft to drive the planetary gear carrier to rotate, while the crankshaft revolves with the planetary gear carrier. At the same time, the crankshaft rotates on its own axis under the combined action of the internal gear ring and the planetary gears, ultimately achieving that the crankshaft rotates relative to the planetary gear carrier while revolving around the carrier, and the cutting part of the cutter head is driven by the crankshaft to move back and forth in a straight line. The first counterweight is provided on the crankshaft, and the second counterweight is provided on the planetary gear carrier. This allows the crankshaft and the planetary gear carrier to counteract lateral excitation when they rotate relative to each other, thereby ensuring good stability of the entire vibration-damping planetary pendulum ring housing during operation.

[0046] Preferably, in this embodiment, the masses of the first counterweight and the second counterweight tend to be close, that is, the masses of the first counterweight and the second counterweight are comparable (or equal).

[0047] Furthermore, such as Figure 1 and Figure 2As shown, the power input shaft 2 and the planetary gear carrier 3 are perpendicular to each other. A first bevel gear 9 is coaxially fixedly mounted on one end of the power input shaft 2 within the housing 1, and a second bevel gear 10 is coaxially fixedly mounted on one end of the planetary gear carrier 3 within the housing 1. The first bevel gear 9 and the second bevel gear 10 mesh with each other. This allows the entire vibration-damping planetary ring housing to achieve vertical reversal in power transmission, and its structure is more compact. Bearings are provided at the rotatable connections of the power input shaft and the housing, the planetary gear carrier and the housing, and the crankshaft and the planetary gear carrier. The use of bearings is a conventional technique in this field and will not be described in detail here.

[0048] like Figure 1 and Figure 2 As shown, in this embodiment, a transmission wheel 21 (which can be a pulley, gear, or sprocket) can also be coaxially fixed at one end of the power input shaft located outside the housing.

[0049] Among them, such as Figure 1 and Figure 2 As shown, the first and second counterweights are staggered along the axial direction of the planetary gear support, so that they do not interfere with each other when rotating.

[0050] Furthermore, such as Figure 2 , Figure 7 and Figure 8 As shown, the crankshaft 4 includes a shaft body 41 and a rocker arm 42. The rocker arm 42 is disposed at one end of the shaft body 41, and the axis of the rocker arm 42 is parallel to and spaced apart from the axis of the shaft body 41. The shaft body 41 extends into the mounting channel 31 and is rotatably connected to the planetary gear support 3. The planetary gears 5 are coaxially and fixedly disposed on the shaft body 41. The rocker arm 42 is located outside the housing 1 and serves as the power output end. This creates a gap between the axis of the rocker arm and the axis of the shaft body, thereby amplifying the amplitude of the cutting blade during reciprocating motion.

[0051] Furthermore, such as Figures 3-6 As shown, the planetary gear support 3 has a notch 32 on the side near the mounting channel 31 that communicates with the interior of the mounting channel 31, and the planetary gear 5 is located within the notch 32. This makes the crankshaft more evenly stressed and less prone to bending and deformation. Blocks 33 are formed at both ends of the planetary gear support corresponding to the notch, and the shaft 41 is rotatably connected to the two blocks 33. The depth of the notch must be sufficient to accommodate the planetary gear and allow it to rotate within it.

[0052] In this embodiment, the structure and assembly relationship of the housing 1, power input shaft 2, planetary gear support 3, crankshaft 4, planetary gear 5, internal gear ring 6, first bevel gear 9 and second bevel gear 10 are all existing technologies. For details, please refer to the contents disclosed in document CN117515113A "A Novel Planetary Gear Swing Ring Box" and CN202790341U "Cutter Drive Device" (although the names of the components are different, the overall structure is similar or the same). The main difference of this utility model is that by adding counterweights to the crankshaft and planetary gear support respectively (the counterweight on the crankshaft is the first counterweight, and the counterweight on the planetary gear support is the second counterweight), the two can achieve dynamic balance when rotating relative to each other, thereby avoiding the lateral excitation generated by the crankshaft when driving the cutting part of the cutting table during reciprocating operation.

[0053] like Figure 3 and Figure 4 As shown, in order to further deviate the center of gravity of the planetary gear support from the installation channel, the weight of the two blocks can be reduced. At the same time, the second counterweight 8 can be placed on the side of the planetary gear support 3 away from the installation channel 31 at the corresponding end (such as reducing the volume of the block and cooperating with the second counterweight, so that the center of gravity of the planetary gear support deviates from the installation channel).

[0054] like Figure 2 As shown, the first counterweight 7 is disposed at the end of the shaft 41 located outside the housing 1, and the first counterweight 7 is located on the side of the shaft 41 away from the swing arm 42 at the corresponding end. This causes the center of gravity of the crankshaft to deviate from the swing arm, thereby reducing the lateral excitation of the crankshaft when driving the cutting table.

[0055] Specifically, in this embodiment, the pitch circle radius of the planetary gear 5 is R, and the pitch circle radius of the internal gear ring 6 is 2R; the distance between the axis of the mounting channel 31 and the axis of the planetary gear support 3 is R; and the distance between the axis of the rocker arm 42 and the axis of the shaft 41 is R. This ensures that when the crankshaft rotates with the planetary gear support, the rocker arm reciprocates in a straight line.

[0056] Among them, such as Figures 2-6 and Figure 8 As shown, since the shaft is coaxially rotated within the mounting channel, the axis of the shaft can be considered to coincide with the axis of the mounting channel. In this case, both axes are represented by a, while the axis of the planetary gear support is represented by b, and the axis of the swing arm is represented by c. That is, the distance between a and b is R, and the distance between a and c is also R.

[0057] The vibration-damping planetary pendulum ring box provided in this embodiment has the following specific features: By installing counterweights on the planetary gear support and crankshaft, when the cutting part of the drive table makes linear reciprocating motion, the center of gravity of the planetary gear support and crankshaft as a whole moves in the opposite direction to the cutting part. This can effectively counteract the excitation of the cutting part's reciprocating motion on the cutting table, reduce the vibration of the cutting table, and improve the reliability of the cutting table.

[0058] like Figures 9-17 As shown, the vibration reduction mechanism of the vibration-damping planetary pendulum ring box provided in this embodiment is as follows: Taking the projection plane of the end of the vibration-damping planetary pendulum ring box near the pendulum arm as a plane, the X-axis is defined by a line parallel to the power input shaft, and the origin is defined by the intersection of the X-axis and the axis of the planetary gear support, forming the Y-axis:

[0059] like Figures 9-13 As shown, when the second counterweight rotates counterclockwise (from 0° to 180°), the first counterweight rotates clockwise, and the swing arm moves horizontally to the right along the X-axis.

[0060] like Figures 14-17 As shown, when the second counterweight rotates counterclockwise (from 180° to 360°), the first counterweight rotates clockwise, and the swing arm moves horizontally to the left along the X-axis;

[0061] The rotational motion of the second and first counterweights can be decomposed into horizontal linear motion along the X-axis and vertical linear motion along the Y-axis. The horizontal motion of the second and first counterweights along the X-axis is opposite to that of the swing arm along the X-axis, which cancels out part of the excitation on the cutting table when the cutting part makes linear reciprocating motion, thus reducing the vibration of the cutting table. The vertical motion of the second counterweight along the Y-axis is opposite to that of the first counterweight along the Y-axis, thus canceling out the excitation along the Y-axis generated during the rotational motion.

[0062] Example 2

[0063] This embodiment provides a cutting table that uses a vibration-damping planetary pendulum ring box as described in Embodiment 1. This cutting table has good stability and low noise during operation.

[0064] Example 3

[0065] This embodiment provides a harvester that uses the header as described in Embodiment 2. The header of this harvester has good stability and low noise during operation.

[0066] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model in any way. Those skilled in the art can readily implement this utility model based on the accompanying drawings and the above description. However, any modifications, alterations, or variations made by those skilled in the art without departing from the scope of the utility model's technical solution, utilizing the disclosed technical content, are equivalent embodiments of this utility model. Furthermore, any equivalent changes, alterations, or variations made to the above embodiments based on the essential technology of this utility model are still within the protection scope of this utility model's technical solution.

Claims

1. A vibration-damping type planetary swing ring box, comprising a box body (1), a power input shaft (2), a planetary wheel support (3) and a crank shaft (4), the power input shaft (2) and the planetary wheel support (3) both penetrate into the box body (1) at one end and are rotationally connected with the box body (1), the power input shaft (2) and the planetary wheel support (3) are drivingly connected at one end in the box body (1), the planetary wheel support (3) has a mounting channel (31) thereon, one end of the crank shaft (4) is located in the mounting channel (31) and is rotationally connected with the planetary wheel support (3), the other end of the crank shaft (4) is located outside the box body (1), the crank shaft (4) is provided with a planetary wheel (5), and the box body (1) is provided with an inner ring gear (6) engaged with the planetary wheel (5), characterized in that, The crank shaft (4) is provided with a first counterweight (7) at the edge of the outer end of the box (1), and the planetary wheel support (3) is provided with a second counterweight (8) at the edge of the outer end of the box (1).

2. The vibration-damping planetary swing ring case according to claim 1, characterized in that, The axes of the mounting channels (31) are parallel to the axes of the planetary wheel supports (3) and are spaced apart, and the centers of gravity of the planetary wheel supports (3) are away from the mounting channels (31).

3. The vibration-reducing planetary ring-and-pinion case of claim 1, wherein, The power input shaft (2) is perpendicular to the planetary wheel supports (3), and the power input shaft (2) is coaxially and fixedly provided with a first umbrella gear (9) at one end in the box (1), the planetary wheel support (3) is coaxially and fixedly provided with a second umbrella gear (10) at one end in the box (1), and the first umbrella gear (9) and the second umbrella gear (10) are engaged with each other.

4. The vibration reduction planetary ring and ball cage of claim 1, wherein, The second counterweight (8) is located on the side away from the mounting channel (31) of the corresponding end of the planetary wheel support (3).

5. The vibration reduction planetary ring and ball cage of claim 1 wherein, The crank shaft (4) comprises a shaft body (41) and a swing arm (42), the swing arm (42) is arranged at one end of the shaft body (41), the axes of the swing arm (42) are parallel to the axes of the shaft body (41) and are spaced apart, the shaft body (41) extends into the mounting channel (31) and is rotationally connected with the planetary wheel support (3), the planetary wheel (5) is coaxially and fixedly arranged on the shaft body (41), and the swing arm (42) is located outside the box (1) as a power output end.

6. The vibration-reducing planetary ring-and-piston case of claim 5, wherein, The first counterweight (7) is arranged at one end of the shaft body (41) outside the box (1), and the first counterweight (7) is located on the side away from the swing arm (42) of the corresponding end of the shaft body (41).

7. The vibration-reducing planetary ring-and-roller cage of claim 1, wherein, The first counterweight (7) and the second counterweight (8) are distributed in a staggered manner in the axial direction of the planetary wheel support (3).

8. The vibration-damping planetary ring-and-gear box according to any one of claims 1-7, characterized in that The planetary wheel support (3) is provided with a notch (32) near the side close to the mounting channel (31), and the notch (32) penetrates the inside of the mounting channel (31), and the planetary wheel (5) is located in the notch (32).

9. A header characterized by, A vibration-damping planetary swing ring box comprising any one of claims 1-8.

10. A harvester characterized by A cutting platform comprising claim 9.

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