Transmission case for horizontal three-rotor devolatilization mixer

Abstract

The invention discloses a transmission case for a horizontal three-rotor devolatilization mixer, which belongs to the technical field of transmission of devolatilization mixers.The transmission case comprises a transmission case body, an input gear shaft is arranged in the transmission case body, a first intermediate gear shaft and a second intermediate gear shaft are arranged on one side of the input gear shaft, and a long output shaft is arranged outside the shaft end of the input gear shaft; transition shafts are arranged on the two sides of the long output shaft, short output shafts are arranged on the outer sides of the two transition shafts, and a transmission stabilizing plate is arranged at the end of the transmission box body. Through the arrangement of the input gear shaft, the first intermediate gear shaft and the second intermediate gear shaft, the tooth number combination of multiple pairs of gears can be changed, wide-range speed regulation can be achieved so as to adapt to different process requirements, through the setting of the specific tooth number ratio, the output shaft can achieve three-shaft same-speed or three-shaft differential-speed operation, and the speed regulation speed is high. The differential mode can generate more complicated material shearing and mixing actions, so that the adaptability of the equipment to a complicated process is greatly enhanced.

Description

Technical Field

[0001] This invention relates to the field of devolve mixing transmission technology, and more particularly to a transmission box for a horizontal three-rotor devolve mixing machine. Background Technology

[0002] In industries related to new polymer materials, rubber, polymers, fibers, and engineering plastics, equipment often encounters the following difficult problems when processing and handling high-viscosity materials: 1. During the stirring process of ultra-high viscosity fluid, adhesion will occur on the cylinder wall and stirring shaft, making it difficult to uniformly mix or transfer heat between ultra-high viscosity fluid and low viscosity fluid in a short period of time. 2. The production process of some materials is complex, and often involves the process of high-viscosity fluids gradually changing from liquid to solid phase. The temperature changes with the reaction conditions, and the viscosity of the material varies greatly, which is difficult for ordinary mixers to adapt to.

[0003] Ordinary mixers suffer from problems such as poor self-cleaning, which leads to material accumulation, resulting in poor product performance consistency. In severe cases, the material forms a "dead zone" inside the drum. If the "dead zone" expands further, the rotating shaft will seize up, making production unsustainable.

[0004] To overcome the shortcomings of existing conventional mixers, such as poor self-cleaning leading to material accumulation and subsequent shaft seizure, a horizontal dual-rotor devolatilization mixer was developed, effectively solving the problems associated with conventional mixers. However, for large-capacity devolatilization applications with high shear requirements, the volume and shearing capacity of the horizontal dual-rotor devolatilization mixer are somewhat insufficient. The horizontal three-rotor devolatilization mixer, with three cavities in a single cylinder section, has a volume 1.5 times that of a single cylinder section of the dual-rotor devolatilization mixer. While dual rotors mesh with only one meshing zone, three rotors mesh with two pairs of each other, resulting in two meshing zones and doubling the shearing capacity. Based on this, a transmission box for the horizontal three-rotor devolatilization mixer is proposed. Summary of the Invention

[0005] The purpose of this invention is to solve the problems in the prior art by proposing a transmission box for a horizontal three-rotor devolatilization mixer.

[0006] To achieve the above objectives, the present invention adopts the following technical solution: A transmission box for a horizontal three-rotor devolatilization mixer includes a transmission box body. An input gear shaft is provided inside the transmission box body. An intermediate gear shaft one and an intermediate gear shaft two are respectively provided on one side of the input gear shaft. A long output shaft is provided outside the shaft end of the input gear shaft. Transition shafts are provided on both sides of the long output shaft. Short output shafts are provided outside the two transition shafts. A transmission stabilizing plate is provided at the end of the transmission box body.

[0007] Preferably, a drive gear is fixed on the input gear shaft, a first driven gear and a first transmission gear are fixed on the first intermediate gear shaft, and a second driven gear and a second transmission gear are fixed on the second intermediate gear shaft. The input gear shaft, the first intermediate gear shaft, and the second intermediate gear shaft are all integral designs of shaft and gear.

[0008] Preferably, the drive gear meshes with the first driven gear, and the first transmission gear meshes with the second driven gear.

[0009] Preferably, a shaft drive gear and a shaft output gear are fixed on the long output shaft, and the second drive gear meshes with the shaft drive gear.

[0010] Preferably, a transition gear is fixed on the transition shaft, a driven output gear is fixed on the short output shaft, the central output gear meshes with the transition gears on both sides, and the transition gear meshes with the driven output gear.

[0011] Preferably, a bushing is provided on the outer wall of the input gear shaft, and an O-ring is installed in the inner hole of the bushing, with the inner hole of the O-ring making transition fit with the outer circle of the input gear shaft.

[0012] Preferably, a skeleton oil seal is installed on the outer wall of the bushing. The O-ring and the skeleton oil seal are used to seal the lubricating oil in the transmission housing, so that the lubricating oil does not leak along the input gear shaft.

[0013] Preferably, two pads are provided on the outer wall of the input gear shaft, and the pads are threaded in the middle. Double-row self-aligning cylindrical roller bearings are installed at both ends of the first intermediate gear shaft, the second intermediate gear shaft, the long output shaft and the two short output shafts. Tapered roller bearings are installed at both ends of the input gear shaft and the two transition shafts.

[0014] Preferably, a plurality of stabilizing plates are fixed inside the transmission housing. The stabilizing plates are used to stabilize the rotation of each shaft component inside the transmission housing. Pipes are installed on the stabilizing plates, and atomizing nozzles are provided on the pipes. A temperature sensor is provided inside the transmission housing.

[0015] Compared with the prior art, the beneficial effects of the present invention are as follows: 1. This solution allows for changing the tooth count combination of multiple gear pairs by setting the input gear shaft, intermediate gear shaft one, and intermediate gear shaft two. This enables a wide range of speed adjustments to adapt to different process requirements. By setting a specific tooth ratio, the output shaft can achieve three-axis simultaneous speed or three-axis differential speed operation. The differential speed mode can generate more complex material shearing and mixing actions, greatly enhancing the equipment's adaptability to complex processes.

[0016] 2. By setting up long and short output shafts, this solution can utilize the specific relationship between the number of spline teeth and the phase at the end of the output shaft to ensure that the stirring claws on the three rotor shafts can mesh precisely during installation, avoiding interference and collisions during operation. This is the key to the safe and stable operation of the equipment.

[0017] 3. This solution utilizes tapered roller bearings and double-row self-aligning cylindrical roller bearings. For input and transition shafts requiring easy disassembly and assembly, tapered roller bearings can withstand combined forces (axial and radial), and their separable inner and outer rings facilitate installation, clearance adjustment, and replacement. For longer shafts such as long output shafts, double-row self-aligning cylindrical roller bearings are used, enabling automatic self-alignment, reducing the requirements for coaxiality machining of the housing bore and shaft, decreasing installation difficulty and cost, while ensuring load-bearing capacity.

[0018] 4. This solution, through the setting of atomizing nozzles, can use temperature sensors to monitor the temperature inside the chamber in real time, and can promptly detect overheating faults caused by abnormal friction. When the temperature rises, the system can promptly start oil mist spraying, which can not only cool down the gears, but also provide lubrication at the same time, effectively reducing friction, preventing wear, maintaining transmission accuracy, and ensuring that the device can operate stably and reliably for a long time under high temperature conditions. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the transmission structure of the transmission box for the horizontal three-rotor devolatilization mixer proposed in this invention; Figure 2 This is a three-dimensional structural schematic diagram of the transmission box for the horizontal three-rotor devolatilization mixer proposed in this invention; Figure 3 This is an overall assembly drawing of the transmission box for the horizontal three-rotor devolatilization mixer proposed in this invention; Figure 4 This is a schematic diagram of the position of the long output shaft in the transmission box of the horizontal three-rotor devolatilization mixer proposed in this invention; Figure 5 This is a schematic diagram of the short output shaft position in the transmission box of the horizontal three-rotor devolatilization mixer proposed in this invention; Figure 6 This is a cross-sectional structural schematic diagram of the transmission box body in the transmission box of the horizontal three-rotor devolatilization mixer proposed in this invention; Figure 7 This is a schematic diagram of the structure of the input gear shaft in the transmission box of the horizontal three-rotor devolatilization mixer proposed in this invention. Figure 8 This is a schematic diagram of the output shaft spline phase in the transmission box of the horizontal three-rotor devolatilization mixer proposed in this invention.

[0020] In the diagram: 1. Input gear shaft; 101. Drive gear; 2. Intermediate gear shaft one; 201. First driven gear; 202. First transmission gear; 3. Intermediate gear shaft two; 301. Second driven gear; 302. Second transmission gear; 4. Long output shaft; 401. Shaft-driven gear; 402. Shaft-output gear; 5. Transition shaft; 501. Transition gear; 6. Short output shaft; 601. Driven output gear; 7. Bushing; 8. O-ring; 9. Oil seal; 10. Tapered roller bearing; 11. Pad; 12. Double-row self-aligning cylindrical roller bearing; 13. Transmission housing; 14. Transmission stabilizing plate; 15. Shaft stabilizing plate; 16. Piping; 17. Atomizing nozzle. Detailed Implementation

[0021] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0022] In the description of this invention, it should be noted that the terms "upper," "lower," "inner," "outer," "top / bottom," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for 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 the invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0023] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installed," "equipped with," "sleeved / connected," "connected," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0024] Example, refer to Figures 1 to 8A transmission box for a horizontal three-rotor devolatilization mixer includes a transmission box body 13. An input gear shaft 1 is installed inside the transmission box body 13. An intermediate gear shaft 1 2 and an intermediate gear shaft 2 3 are respectively installed on one side of the input gear shaft 1. A long output shaft 4 is installed outside the shaft end of the input gear shaft 1. Transition shafts 5 are installed on both sides of the long output shaft 4. Short output shafts 6 are installed outside the two transition shafts 5. A transmission stabilizing plate 14 is installed at the end of the transmission box body 13. Furthermore, a drive gear 101 is fixed on the input gear shaft 1, a first driven gear 201 and a first transmission gear 202 are fixed on the intermediate gear shaft 1, and a second driven gear 301 and a second transmission gear 302 are fixed on the intermediate gear shaft 2. The input gear shaft 1, intermediate gear shaft 1, and intermediate gear shaft 2 are all integrated shaft and gear designs. The drive gear 101 meshes with the first driven gear 201, and the first transmission gear 202 meshes with the second driven gear 301. A shaft-driven transmission gear 401 and a shaft-driven output gear 402 are fixed on the long output shaft 4, and the second transmission gear 302 meshes with the shaft-driven transmission gear 401. A transition gear 501 is fixed on the transition shaft 5, and a driven output gear 601 is fixed on the short output shaft 6. The shaft-driven output gear 402 meshes with the transition gears 501 on both sides, and the transition gears 501 mesh with the driven output gear 601. It should be noted that: the external motor transmits the speed and torque to the input gear shaft 1 through a coupling. The speed and torque are then transmitted to the long output shaft 4 through the meshing of three pairs of gears: the drive gear 101, the first driven gear 201, the first transmission gear 202, the second driven gear 301, the second transmission gear 302, and the shaft transmission gear 401. After three-stage reduction, the speed is transmitted to the two short output shafts 6 through two transition gears 501 on the two transition shafts 5. By changing the number of teeth of the drive gear 101, the first driven gear 201, the first transmission gear 202, the second driven gear 301, the second transmission gear 302, and the shaft transmission gear 401, various speed ratios can be obtained, achieving the design goal of a wide speed range and adjustable speed ratio. When the number of teeth on the central output gear 402 and the driven output gear 601 is the same, the long output shaft 4 and the two short output shafts 6 rotate at the same speed. When the ratio of the number of teeth on the central output gear 402 to the driven output gear 601 is 4 / 5 or 5 / 4, the long output shaft 4 and the two short output shafts 6 rotate at different speeds, i.e., differential speed. The speed ratio of the three shafts is 4:5:4 or 5:4:5. This achieves the design objective of allowing the three output shafts to rotate at the same speed or to be changed to differential speed. The ends of the long output shaft 4 and the two short output shafts 6 are all involute splines with identical spline parameters. They are connected to the three rotor shafts of the horizontal three-rotor devolatilization mixer via spline sleeves. Stirring claws are welded onto the three rotor shafts. When the three rotor shafts are running, the stirring claws on the three shafts mesh with each other and can clean the material adhering to the stirring claws. The relative positions of the stirring claws are required when the three shafts are initially installed. Otherwise, when the three rotor shafts are running, the stirring claws on the three shafts cannot mesh correctly, resulting in mutual interference. The initial phase of the three rotor shafts is ensured by controlling the relative positions of the spline teeth on the long output shaft 4 and the two short output shafts 6. When the number of spline teeth is a multiple of four, the spline teeth on the long output shaft 4 and the two short output shafts 6 are in the same position, that is, the phase difference between the three is zero degrees. When the number of spline teeth is not a multiple of four, when the spline teeth on one shaft are in a vertical position, the spline teeth on the other shaft must be in a horizontal position, that is, the phase difference between the two shafts is 90 degrees.

[0025] The advantages mentioned above are: by selecting a reasonable three-stage reduction scheme, the speed range is wide and the speed ratio is adjustable, realizing one shaft input and three shafts rotating in the same direction for output. According to process requirements, the three output shafts can be at the same speed or can be changed to differential speed, making the transmission device more versatile. A bushing 7 is provided on the outer wall of the input gear shaft 1, and an O-ring 8 is installed in the inner hole of the bushing 7. The inner hole of the O-ring 8 is in transition fit with the outer circle of the input gear shaft 1.

[0026] Furthermore, a skeleton oil seal 9 is installed on the outer wall of the bushing 7. The O-ring 8 and the skeleton oil seal 9 are used to seal the lubricating oil in the transmission housing 13 in the housing so that the lubricating oil does not leak along the input gear shaft 1. Two pads 11 are provided on the outer wall of the input gear shaft 1. The pads 11 are threaded in the middle. Double row self-aligning cylindrical roller bearings 12 are installed at both ends of the intermediate gear shaft 1 2, intermediate gear shaft 2 3, long output shaft 4 and two short output shafts 6. Tapered roller bearings 10 are installed at both ends of the input gear shaft 1 and the two transition shafts 5. It should be noted that the input gear shaft 1 and the two transition shafts 5 are supported at both ends by tapered roller bearings 10. The tapered roller bearings 10 can withstand both axial and radial forces. The tapered roller bearings 10 are inner and outer ring separable bearings, which makes it easy to install and disassemble the input gear shaft 1 and to adjust the bearing clearance. The bushing 7 undergoes heat treatment, resulting in an outer surface hardness of HRC60~62. This high hardness provides excellent wear resistance and a long service life. Replacement is also convenient when the bushing 7 eventually wears out. This design prevents the input gear shaft 1 from failing due to wear. The pad 11 has a threaded center. After disassembling the input gear shaft 1, the outer ring of the tapered roller bearing 10 remains in the inner hole of the transmission housing 13. The long screw is screwed into the threaded hole in the center of the pad 11, and the long screw is pulled outward to pull the pad 11 out of the housing. This allows the outer ring of the tapered roller bearing 10 to be pulled out of the inner hole of the housing. The intermediate gear shaft 1 2, intermediate gear shaft 2 3, long output shaft 4 and two short output shafts 6 are supported at both ends by double row self-aligning cylindrical roller bearings 12. The double row self-aligning cylindrical roller bearings 12 can withstand both axial and radial forces. The double row self-aligning cylindrical roller bearings 12 are installed in pairs, which allows for a slight amount of shaft wobble. This reduces the coaxiality requirement at both ends of the shaft and also reduces the coaxiality requirement of the bearing mounting holes at both ends. Based on the above advantages, the following measures were taken: a suitable bearing type was selected, and the bearings arranged on the parting surface of the transmission housing 13 were selected to be double-row self-aligning cylindrical roller bearings 12 installed in pairs. The input gear shaft 1 and the transition shaft 5 were both installed in the lower housing. The tapered roller bearings 10 used ensured convenient installation. The central threaded pad 11 added to it made the disassembly and assembly of the outer ring of the tapered roller bearing 10 more convenient. Furthermore, multiple stabilizing plates 15 are fixed inside the transmission housing 13. The stabilizing plates 15 are used to stabilize the rotation of each shaft component inside the transmission housing 13. Pipes 16 are installed on the stabilizing plates 15, and atomizing nozzles 17 are provided on the pipes 16. A temperature sensor is provided inside the transmission housing 13. It should be noted that the temperature sensor installed in the transmission housing 13 can monitor the temperature inside the housing in real time during operation. If the temperature inside the housing rises rapidly, it indicates that the meshing transmission between the gears in the transmission housing 13 has generated a large amount of heat, that is, there is a large amount of friction in the meshing transmission between the gears. In order to avoid wear and insufficient transmission accuracy caused by the meshing transmission of high-temperature gears under large friction, cooling oil is introduced into the pipeline 16 and sprayed out through the atomizing nozzle 17 to spray the tooth surface of each gear, so that each gear can be cooled and lubricated, thereby reducing the friction of the meshing transmission between the gears. The advantages mentioned above are as follows: when the gears in the transmission housing 13 generate a lot of heat due to transmission friction, cooling oil can be sprayed onto the meshing tooth surfaces of each gear in a timely manner to cool them down quickly and reduce the transmission friction between the gears, thus ensuring the stability and reliability of the transmission. In use, the external motor transmits the speed and torque to the input gear shaft 1 via a coupling. Through the meshing of three pairs of gears—drive gear 101, first driven gear 201, first transmission gear 202, and second driven gear 301, second transmission gear 302, and shaft transmission gear 401—the speed and torque are reduced in three stages and then transmitted to the long output shaft 4. This speed and torque are then transmitted to the two short output shafts 6 via two transition gears 501 on two transition shafts 5. The speed and torque are further reduced by changing the positions of the drive gear 101, first driven gear 201, first transmission gear 202, and second transmission gear 302. The number of teeth on the driven gear 301, the second transmission gear 302, and the shaft transmission gear 401 can achieve various speed ratios, thus achieving a wide speed range and adjustable speed ratios. When the number of teeth on the shaft output gear 402 and the driven output gear 601 is the same, the long output shaft 4 and the two short output shafts 6 rotate at the same speed. When the tooth ratio between the shaft output gear 402 and the driven output gear 601 is 4 / 5 or 5 / 4, the long output shaft 4 and the two short output shafts 6 rotate at different speeds, i.e., differential speed. The speed ratio of the three shafts is 4:5:4 or 5:4:5. This achieves the design objective of allowing the three output shafts to rotate at the same speed or to be changed to differential speed. The ends of the long output shaft 4 and the two short output shafts 6 are all involute splines with identical spline parameters. They are connected to the three rotor shafts of the horizontal three-rotor devolatilization mixer via spline sleeves. Stirring claws are welded on the three rotor shafts. When the three rotor shafts are running, the stirring claws on the three shafts mesh with each other and can clean the material adhering to the stirring claws. The relative positions of the stirring claws are required when the three shafts are initially installed. Otherwise, when the three rotor shafts are running, the stirring claws on the three shafts cannot mesh properly, resulting in mutual interference. The initial phase of the three rotor shafts is ensured by controlling the relative positions of the spline teeth on the long output shaft 4 and the two short output shafts 6. When the number of spline teeth is a multiple of four, the spline teeth on the long output shaft 4 and the two short output shafts 6 are in the same position, that is, the phase difference between the three is zero degrees. When the number of spline teeth is not a multiple of four, when the spline teeth on one shaft are in a vertical position, the spline teeth on the other shaft must be in a horizontal position, that is, the phase difference between the two shafts is 90 degrees. By selecting a reasonable three-stage reduction scheme, the speed range is wide and the speed ratio is adjustable, realizing one shaft input and three shafts rotating in the same direction for output. According to process requirements, the three output shafts can be at the same speed or changed to differential speed, making the transmission device more versatile. The input gear shaft 1 and the two transition shafts 5 are supported at both ends by tapered roller bearings 10. The tapered roller bearings 10 can withstand both axial and radial forces. The tapered roller bearings 10 are separable bearings with inner and outer rings, which makes it easy to install and remove the input gear shaft 1 and adjust the bearing clearance. The bushing 7 is heat-treated, and the surface hardness of the outer circle reaches HRC60~62. It has high hardness, good wear resistance, and long service life. It is also easy to replace the bushing 7 when it eventually wears out. This design avoids failure of the input gear shaft 1 due to wear. The pad 11 is threaded in the middle. After the input gear shaft 1 is removed, the outer ring of the tapered roller bearing 10 remains in the inner hole of the transmission housing 13. The long screw is screwed into the middle screw hole of the pad 11, and the long screw is pulled to pull the pad 11 outward, thereby pulling the outer ring of the tapered roller bearing 10 out of the inner hole of the housing. The intermediate gear shaft 1 (2), intermediate gear shaft 2 (3), long output shaft 4, and two short output shafts 6 are supported at both ends by double-row self-aligning cylindrical roller bearings (12). The double-row self-aligning cylindrical roller bearings (12) can withstand both axial and radial forces. The double-row self-aligning cylindrical roller bearings (12) are installed in pairs, allowing for a slight amount of shaft wobble. This reduces the coaxiality requirements at both ends of the shaft and also reduces the coaxiality requirements of the bearing mounting holes at both ends. A suitable bearing type was selected, and the bearings arranged on the parting surface of the transmission housing 13 are selected to be double-row self-aligning cylindrical roller bearings (12) installed in pairs. The input gear shaft 1 and the transition shaft 5 are both installed in the lower housing. The tapered roller bearings (10) used ensure convenient installation. The added central threaded pad (11) makes it easier to disassemble and assemble the outer ring of the tapered roller bearing (10). The temperature sensor installed in the transmission housing 13 can monitor the temperature inside the housing in real time during operation. If the temperature inside the housing rises rapidly, it indicates that the meshing transmission between the gears in the transmission housing 13 has generated a large amount of heat, meaning that there is significant friction in the meshing transmission between the gears. To avoid wear and insufficient transmission accuracy caused by the high-temperature gears meshing under high friction, cooling oil is introduced into the pipeline 16 and atomized and sprayed out through the atomizing nozzle 17 to spray the tooth surfaces of each gear, so that each gear can be cooled and lubricated, thereby reducing the temperature of each gear and decreasing the meshing transmission friction between the gears. In this way, when the gears in the transmission housing 13 generate a large amount of heat due to friction, cooling oil can be sprayed onto the meshing tooth surfaces of each gear in a timely manner to quickly cool down the gears and reduce the transmission friction between the gears, ensuring stable and reliable transmission.

[0027] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A transmission box for a horizontal three-rotor devolatilization mixer, comprising a transmission box body (13), characterized in that, The transmission housing (13) is provided with an input gear shaft (1), and an intermediate gear shaft one (2) and an intermediate gear shaft two (3) are respectively provided on one side of the input gear shaft (1). A long output shaft (4) is provided on the outside of the shaft end of the input gear shaft (1). A transition shaft (5) is provided on both sides of the long output shaft (4). A short output shaft (6) is provided on the outside of the two transition shafts (5). A transmission stabilizing plate (14) is provided at the end of the transmission housing (13).

2. The transmission box for the horizontal three-rotor devolatilization mixer according to claim 1, characterized in that, The input gear shaft (1) is fixed with a drive gear (101), the intermediate gear shaft one (2) is fixed with a first driven gear (201) and a first transmission gear (202), and the intermediate gear shaft two (3) is fixed with a second driven gear (301) and a second transmission gear (302). The input gear shaft (1), intermediate gear shaft one (2) and intermediate gear shaft two (3) are all integrated shaft and gear designs.

3. The transmission box for the horizontal three-rotor devolatilization mixer according to claim 2, characterized in that, The drive gear (101) meshes with the first driven gear (201), and the first transmission gear (202) meshes with the second driven gear (301).

4. The transmission box for the horizontal three-rotor devolatilization mixer according to claim 2, characterized in that, The long output shaft (4) is fixed with a shaft drive gear (401) and a shaft output gear (402), and the second drive gear (302) meshes with the shaft drive gear (401).

5. The transmission box for the horizontal three-rotor devolatilization mixer according to claim 4, characterized in that, A transition gear (501) is fixed on the transition shaft (5), and a driven output gear (601) is fixed on the short output shaft (6). The shaft output gear (402) meshes with the transition gears (501) on both sides respectively, and the transition gear (501) meshes with the driven output gear (601).

6. The transmission box for the horizontal three-rotor devolatilization mixer according to claim 1, characterized in that, A bushing (7) is provided on the outer wall of the input gear shaft (1), and an O-ring (8) is installed in the inner hole of the bushing (7). The inner hole of the O-ring (8) is in transition fit with the outer circle of the input gear shaft (1).

7. The transmission box for the horizontal three-rotor devolatilization mixer according to claim 6, characterized in that, A skeleton oil seal (9) is installed on the outer wall of the bushing (7). The O-ring (8) and the skeleton oil seal (9) are used to seal the lubricating oil in the transmission housing (13) in the housing so that the lubricating oil does not leak along the input gear shaft (1).

8. The transmission box for the horizontal three-rotor devolatilization mixer according to claim 1, characterized in that, Two pads (11) are provided on the outer side wall of the input gear shaft (1). The pads (11) are threaded in the middle. Double-row self-aligning cylindrical roller bearings (12) are installed at both ends of the intermediate gear shaft one (2), intermediate gear shaft two (3), long output shaft (4) and two short output shafts (6). Tapered roller bearings (10) are installed at both ends of the input gear shaft (1) and the two transition shafts (5).

9. The transmission box for the horizontal three-rotor devolatilization mixer according to claim 1, characterized in that, Multiple stabilizing plates (15) are fixed inside the transmission housing (13). The stabilizing plates (15) are used to stabilize the rotation of each shaft component inside the transmission housing (13). Pipes (16) are installed on the stabilizing plates (15). Atomizing nozzles (17) are provided on the pipes (16). A temperature sensor is provided inside the transmission housing (13).

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