A power split gearbox

Abstract

This utility model relates to a power split gearbox, including a transmission stage and a power split output section within a gearbox housing. It comprises: a first output shaft extending axially from the gearbox housing, equipped with a synchronously rotating first output shaft gear; a first split shaft rotatably disposed within the gearbox housing, equipped with a synchronously rotating first split gear and a first transition gear downstream in the transmission direction, wherein torque is transmitted from the first output shaft to the first split shaft via a pair of meshing first output shaft gears and first split gears; and a second output shaft extending axially from the gearbox housing, equipped with a synchronously rotating second output shaft gear, wherein the first transition gear and the second output shaft gear are connected to transmit torque from the first split shaft to the second output shaft; the center distance between the first output shaft and the first split shaft, and the center distance between the first split shaft and the second output shaft, are greater than the center distance between the first and second output shafts. This utility model outputs high torque with a small center distance output shaft.

Description

Technical Field

[0001] This utility model relates to a power split gearbox, and more particularly to a power split gearbox that outputs a large torque with a small center distance of the output shaft. Background Technology

[0002] In the application of molten pump reducers, the two output shafts often face the problem of small center distance. This problem is particularly significant in high-power models, resulting in certain design bottlenecks for some high-power molten pump reducers with small center distance.

[0003] Currently, the steps to solve this problem are as follows: Design a pair of meshing gear shafts with a speed ratio of 1 based on the center distance requirement of the two output shafts; increase the tooth width to meet the design requirements of improving the safety factor of the gear shaft teeth; and check the bearing life on the two output shafts.

[0004] The current solution has the following drawbacks: In the current transmission form, because the center distance of the output shaft is given by the working machine, the only way to improve the safety factor of the teeth under high torque output is to increase the tooth width of the last stage. In many high torque designs, the ratio of tooth width to center distance is too large, which affects the load distribution in the tooth width direction of the transmission stage. This results in more cost investment in the machining process to strictly control the accuracy errors of various gears.

[0005] Therefore, it is necessary to design a gearbox that can output large torque with a small center distance of the output shaft to solve one or more of the above-mentioned technical defects. Utility Model Content

[0006] To overcome at least one of the defects of the prior art, this utility model provides a power split gearbox capable of outputting large torque.

[0007] According to one aspect of the present invention, a power split gearbox is provided, comprising:

[0008] The transmission stage located within the gearbox housing; and

[0009] A power shunt output section that receives the torque transmitted by the transmission stage and outputs the torque to the outside of the gearbox.

[0010] The power shunt output section includes:

[0011] A first output shaft extends axially from the gearbox housing, and a first output shaft gear capable of rotating synchronously with the first output shaft is provided on the first output shaft;

[0012] A first splitter shaft is rotatably disposed within the gearbox housing. A first splitter gear capable of rotating synchronously with the first splitter shaft and a first transition gear located downstream of the first splitter gear in the transmission direction are provided on the first splitter shaft. Torque is transmitted from the first output shaft to the first splitter shaft via a pair of meshing first output shaft gears and the first splitter gear.

[0013] A second output shaft extends from the gearbox housing along the axial direction, and a second output shaft gear is provided on the second output shaft that can rotate synchronously with the second output shaft, wherein the first transition gear is drivenly connected to the second output shaft gear to transmit torque from the first split shaft to the second output shaft;

[0014] The center distance between the first output shaft and the first shunt shaft, and the center distance between the first shunt shaft and the second output shaft are both greater than the center distance between the first output shaft and the second output shaft.

[0015] According to one embodiment, the power shunt output section further includes a second shunt shaft rotatably disposed within the gearbox housing, and a second shunt gear capable of rotating synchronously with the second shunt shaft is provided on the second shunt shaft, wherein the first transition gear meshes with the second shunt gear or with a second transition gear located upstream of the second shunt gear in the transmission direction on the second shunt shaft to transmit torque from the first shunt shaft to the second shunt shaft, and the second shunt gear meshes with the second output shaft gear to transmit torque from the second shunt shaft to the second output shaft.

[0016] According to one embodiment, the total transmission ratio from the first output shaft to the second output shaft via the first split shaft and the second split shaft is 1.

[0017] According to one embodiment, the center distance between the first output shaft and the first shunt shaft, the center distance between the first shunt shaft and the second shunt shaft, and the center distance between the second shunt shaft and the second output shaft are all equal to each other.

[0018] According to one embodiment, the transmission ratio of the first output shaft and the first split shaft, the transmission ratio of the first split shaft and the second split shaft, and the transmission ratio of the second split shaft and the second output shaft are all 1.

[0019] According to one embodiment, one of the transmission ratios of the first output shaft and the first split shaft, the first split shaft and the second split shaft, and the second split shaft and the second output shaft is 1.

[0020] According to one embodiment, the transmission ratio between the first output shaft and the first split shaft, and the transmission ratio between the first split shaft and the second output shaft are both 1.

[0021] According to one embodiment, the first output shaft, the first shunt shaft, the second shunt shaft, and the second output shaft are arranged parallel to each other.

[0022] According to one embodiment, the plane containing the first output shaft and the first shunt shaft is orthogonal to the plane containing the first shunt shaft and the second shunt shaft, and the plane containing the first output shaft and the first shunt shaft is orthogonal to the plane containing the first output shaft and the second output shaft.

[0023] According to one embodiment, each gear in the power shunt output section is one of a cylindrical spur gear, a cylindrical helical gear, or a herringbone gear composed of a pair of cylindrical helical gears with opposite directions of rotation, and / or, the power shunt gearbox is a reducer for a molten pump.

[0024] This invention modifies the split transmission form of the two output shafts in the final stage. By adding a split shaft instead of directly meshing the two output shafts, it enables high-power models to output large torque while the gear teeth are evenly loaded in the tooth width direction. Attached Figure Description

[0025] Specific details of various embodiments of the present invention are illustrated in the accompanying drawings and the following description, from which other features and advantages of the present invention will become apparent.

[0026] Figure 1 This is a schematic front view of the power shunt output section in a power shunt gearbox according to an embodiment of the present invention.

[0027] Figure 2 yes Figure 1 A schematic side view of one embodiment of the power shunt output section shown.

[0028] Figure 3 yes Figure 1 A schematic side view of another embodiment of the power shunt output section shown. Detailed Implementation

[0029] The specific embodiments and variations thereof according to the present invention will now be described in detail with reference to the accompanying drawings.

[0030] For ease of description, spatial relative terms such as "inner," "outer," "upper," "lower," "front," "rear," "left," "right," "top," and "bottom" are used in this document to define the various components and their connection relationships. However, this is not intended to be limiting. When the placement of the components changes, these spatial relative relationships can also be reversed or altered without affecting the scope of protection of this utility model.

[0031] Figure 1 This is a schematic front view of the power shunt output section in a gearbox according to one embodiment of the present invention. In this embodiment, the gearbox is, for example, a reducer for a molten metal pump. However, it is conceivable that the gearbox could also be a gearbox with other uses.

[0032] The power-splitting gearbox includes a housing (not shown), a transmission stage (not shown) located within the housing, and a power-splitting output section (e.g., the one that outputs the torque transmitted by the transmission stage). Figure 1 (As shown). This transmission stage can be a single or multi-stage planetary transmission stage or other transmission forms. The power split output section is used to output the torque from the gearbox to the working machine via the output shaft.

[0033] like Figure 1 As shown, the power shunt output section includes a first output shaft 1 and a second output shaft 2 extending axially out of the housing. The center distance d between the first output shaft 1 and the second output shaft 2 is set to meet the input requirements of the working machine. This center distance d is usually a fixed value for the same type of working machine; however, the value of the center distance d can vary depending on the different input requirements of different working machines.

[0034] When the center distance *d* between the first output shaft 1 and the second output shaft 2 of a gearbox is small but a large torque output is required, a power shunt stage is provided between the first output shaft 1 and the second output shaft 2 to divert the torque transmitted from the transmission stage, so that larger gears can be used to withstand greater loads. Typically, the first output shaft 1 and the second output shaft 2 are required to rotate at the same speed, with each outputting 50% of the torque. Therefore, the overall transmission ratio from the first output shaft 1 to the second output shaft 2 via the power shunt stage is 1. However, the torque distribution between the first output shaft 1 and the second output shaft 2 can vary depending on the specific requirements of the working machine.

[0035] exist Figure 1 In the illustrated embodiment, a first output shaft gear 11 is provided on the first output shaft 1, which can rotate together with it. The first output shaft gear 11 can be integrally formed with the first output shaft 1, or it can be a separate gear mounted to the first output shaft 1. In the case of being a separate gear, the first output shaft gear 11 can be mounted to the first output shaft 1 through a keyway fit, preferably through a flat key fit.

[0036] The power shunt stage between the first output shaft 1 and the second output shaft 2 includes a first shunt shaft 3 and a second shunt shaft 4. The first output shaft 1, the first shunt shaft 3, the second shunt shaft 4, and the second output shaft 2 are sequentially connected for transmission, diverting the torque transmitted from the transmission stage to the first output shaft 1 to the second output shaft 2. Depending on the space requirements within the gearbox, more shunt shafts can be used to transmit torque.

[0037] The first splitter shaft 3 is provided with a first splitter gear 31 that rotates with it. This first splitter gear 31 is paired with and meshes with the first output shaft gear 11. In order to transmit greater torque, the first center distance a1 between the first output shaft 1 and the first splitter shaft 3 is greater than the center distance d between the first output shaft 1 and the second output shaft 2, thereby allowing the use of a larger gear that can transmit greater torque. Similar to the first output shaft gear 11 described above, the first splitter gear 31 can be integrally formed with the first splitter shaft 3, or it can be mounted to the first splitter shaft 3, for example, by means of a flat key.

[0038] like Figure 2 As shown, a first transition gear 32 is provided on the first splitting shaft 3 at a position axially spaced from the first splitting gear 31. This first transition gear 32 is located downstream of the first splitting gear 31 in the transmission direction and can rotate synchronously with the first splitting shaft 3 to interact with the second splitting gear 41 or the second transition gear 42 on the second splitting shaft 4 (described later). Figure 3 The first transition gear 32 engages with the first split shaft 3 to transmit the torque of the first split shaft 3 to the second split shaft 4. Similarly, the first transition gear 32 can be integrally formed with the first split shaft 3, or it can be mounted to the first split shaft 3, for example, by means of a flat key.

[0039] The second splitter shaft 4 is provided with a second splitter gear 41 that can rotate with it. The second splitter gear 41 is paired with and meshes with the first transition gear 32 on the first splitter shaft 3. Figure 2 As shown. Alternatively, as Figure 3 As shown, a second transition gear 42, which rotates together with the second split shaft 4, may also be provided on the second split shaft 4. This second transition gear 42 is located upstream of the second split gear 41 in the transmission direction and is paired with and meshes with the first transition gear 32 on the first split shaft 3. The second split gear 41 meshes with the second output shaft gear 21 on the second output shaft 2, which will be described later. Figure 1 As shown, the second split shaft 4 and the first split shaft 3 have a second center distance a2. Similarly, in order to transmit greater torque, this second center distance a2 is also greater than the center distance d between the first output shaft 1 and the second output shaft 2. In addition, the second split gear 41 and / or the second transition gear 42 can be integrally formed with the second split shaft 4, or can be mounted to the second split shaft 4, for example, by means of a flat key.

[0040] Continue to refer to Figure 1 The second output shaft 2 is provided with a second output shaft gear 21 that rotates with it. This second output shaft gear 21 is paired with and meshes with a second branch gear 41 on the second branch shaft 4 to receive torque from the second branch shaft 4. A third center distance a3 exists between the second output shaft 2 and the second branch shaft 4. Similarly, to transmit greater torque, this third center distance a3 is also greater than the center distance d between the first output shaft 1 and the second output shaft 2. Furthermore, the second output shaft gear 21 can be integrally formed with the second output shaft 2, or it can be mounted to the second output shaft 2, for example, via a flat key.

[0041] By setting a power shunt stage between the first output shaft 1 and the second output shaft 2, the torque transmitted by the transmission stages within the gearbox can be shunted, preventing direct meshing between the first output shaft 1 and the second output shaft 2. When the first output shaft 1 and the second output shaft 2 have a small center distance but require high torque output, this shunt can increase the center distances of the shunt stages located between the first output shaft 1 and the second output shaft 2 in the transmission direction. These center distances can be adjusted within a certain range, allowing for the use of larger gears, improving gear safety, ensuring the ratio of tooth width to center distance is within a relatively reasonable range, and thus guaranteeing the load-sharing performance of the tooth surface in the tooth width direction. Furthermore, the lifespan of the bearings supporting the rotation of each transmission shaft within the shunt stage is checked to meet operational requirements.

[0042] exist Figure 1 In the illustrated embodiment, to maximize space saving, the first output shaft 1, the first branch shaft 3, the second branch shaft 4, and the second output shaft 2 are arranged parallel to each other. Preferably, the first center distance a1 between the first output shaft 1 and the first branch shaft 3, the second center distance a2 between the first branch shaft 3 and the second branch shaft 4, and the third center distance a3 between the second branch shaft 4 and the second output shaft 2 are all equal. The transmission ratios from the first output shaft 1 to the first branch shaft 3, from the first branch shaft 3 to the second branch shaft 4, and from the second branch shaft 4 to the second output shaft 2 are all 1 or approximately 1, thereby enabling the transmission of greater torque compared to direct meshing of the first output shaft 1 and the second output shaft 2. Figure 1As shown, the plane containing the first output shaft 1 and the first branch shaft 3 is orthogonal to the plane containing the first branch shaft 3 and the second branch shaft 4. The plane containing the first branch shaft 3 and the second branch shaft 4 intersects the plane containing the second branch shaft 4 and the second output shaft 2 at an angle. The plane containing the second branch shaft 4 and the second output shaft 2 intersects the plane containing the first output shaft 1 and the second output shaft 2 at an angle. The plane containing the first output shaft 1 and the second output shaft 2 is orthogonal to the plane containing the first output shaft 1 and the first branch shaft 3. For example, the first output shaft 1 and the first branch shaft 3 are located in the same horizontal plane, the first branch shaft 3 and the second branch shaft 4 are located in the same vertical plane, the second branch shaft 4 and the second output shaft 2 are located in an inclined plane, and the first output shaft 1 and the second output shaft 2 are located in the same vertical plane.

[0043] Although the above description states that the respective center distances of the power shunt stages are equal to each other, these center distances can also be unequal to each other, or in other words, the respective transmission ratios can be different from 1. For example, the respective center distances and transmission ratios can be set such that in the power shunt stage from the first output shaft 1 to the second output shaft 2, the respective transmission ratios can be less than 1 and then greater than 1, preferably greater than 1 and then less than 1, thereby ensuring that the power transmitted to the second output shaft 2 meets the requirements of the driven machine.

[0044] Additionally, the second splitter shaft 4 serves to adjust the direction of rotation of the second output shaft 2. If the two output shafts rotate in the same direction, the second splitter shaft 4 can be removed, meaning the first transition gear 32 on the first splitter shaft 3 directly meshes with the second output shaft gear 21. Preferably, the transmission ratio between the first output shaft 1 and the first splitter shaft 3, and the transmission ratio between the first splitter shaft 3 and the second output shaft 2, are both 1.

[0045] In addition, the gears on the first output shaft 1, the first split shaft 3, the second split shaft 4 and the second output shaft 2 are preferably cylindrical gears. As needed, spur gears, helical gears or herringbone gears composed of a pair of gears with opposite directions of rotation but the same other parameters can be selected.

[0046] The specific embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the specific structures described above, but covers various modifications and equivalent features. Those skilled in the art can make various changes without departing from the protection scope of the present invention.

Claims

1. A power split gearbox, comprising: The transmission stage is located inside the gearbox housing; and A power shunt output section that receives the torque transmitted by the drive stage and outputs the torque to the outside of the gearbox. The power shunt output section is characterized by comprising: A first output shaft (1) extends axially from the gearbox housing, and a first output shaft gear (11) is provided on the first output shaft (1) that can rotate synchronously with the first output shaft (1); A first split shaft (3) is rotatably disposed within the gearbox housing. A first split gear (31) capable of rotating synchronously with the first split shaft (3) and a first transition gear (32) located downstream of the first split gear (31) in the transmission direction are provided on the first split shaft (3). Torque is transmitted from the first output shaft (1) to the first split shaft (3) via a pair of meshing first output shaft gears (11) and the first split gear (31). A second output shaft (2) extends out of the gearbox housing along the axial direction. A second output shaft gear (21) is provided on the second output shaft (2) and can rotate synchronously with the second output shaft (2). The first transition gear (32) is connected to the second output shaft gear (21) to transmit torque from the first split shaft (3) to the second output shaft (2). The center distance between the first output shaft (1) and the first split shaft (3) and the center distance between the first split shaft (3) and the second output shaft (2) are both greater than the center distance between the first output shaft (1) and the second output shaft (2).

2. The power split gearbox according to claim 1, characterized in that, The power split output section further includes a second split shaft (4) rotatably disposed within the gearbox housing. A second split gear (41) capable of rotating synchronously with the second split shaft (4) is provided on the second split shaft (4). The first transition gear (32) meshes with the second split gear (41) or with the second transition gear (42) located upstream of the second split gear (41) in the transmission direction on the second split shaft (4) to transmit torque from the first split shaft (3) to the second split shaft (4). The second split gear (41) meshes with the second output shaft gear (21) to transmit torque from the second split shaft (4) to the second output shaft (2).

3. The power split gearbox according to claim 2, characterized in that, The total transmission ratio from the first output shaft (1) to the second output shaft (2) via the first split shaft (3) and the second split shaft (4) is 1.

4. The power split gearbox according to claim 3, characterized in that, The center distance between the first output shaft (1) and the first split shaft (3), the center distance between the first split shaft (3) and the second split shaft (4), and the center distance between the second split shaft (4) and the second output shaft (2) are all equal.

5. The power split gearbox according to claim 4, characterized in that, The transmission ratios of the first output shaft (1) and the first split shaft (3), the first split shaft (3) and the second split shaft (4), and the second split shaft (4) and the second output shaft (2) are all 1.

6. The power split gearbox according to claim 3, characterized in that, One of the transmission ratios of the first output shaft (1) and the first split shaft (3), the first split shaft (3) and the second split shaft (4), and the second split shaft (4) and the second output shaft (2) is 1.

7. The power split gearbox according to claim 1, characterized in that, The transmission ratio of the first output shaft (1) and the first split shaft (3), and the transmission ratio of the first split shaft (3) and the second output shaft (2) are both 1.

8. The power split gearbox according to any one of claims 2-6, characterized in that, The first output shaft (1), the first split shaft (3), the second split shaft (4) and the second output shaft (2) are arranged in parallel to each other.

9. The power split gearbox according to any one of claims 2-6, characterized in that, The plane containing the first output shaft (1) and the first split shaft (3) is orthogonal to the plane containing the first split shaft (3) and the second split shaft (4), and the plane containing the first output shaft (1) and the first split shaft (3) is orthogonal to the plane containing the first output shaft (1) and the second output shaft (2).

10. The power split gearbox according to any one of claims 1-7, characterized in that, Each gear in the power shunt output section is one of a cylindrical spur gear, a cylindrical helical gear, or a herringbone gear composed of a pair of cylindrical helical gears with opposite directions of rotation, and / or the power shunt gearbox is a reducer for a molten pump.

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