Anti-abrasion transmission structure for tail end of screw shaft of preheater

Abstract

The utility model relates to the technical field of carbon anode manufacturing, and discloses a preheater screw shaft tail end anti-abrasion transmission structure which comprises a screw shaft and a transmission mechanism used for driving the screw shaft to rotate, a graphite bearing used for supporting the screw shaft is arranged at the tail end of the screw shaft, and an anti-abrasion shaft sleeve is arranged between the tail end of the screw shaft and the graphite bearing. A plurality of fixing holes used for being fixed to the tail end of the spiral shaft are evenly distributed in the two ends of the wear-resisting shaft sleeve in the circumferential direction. The technical problem that in the prior art, due to contact abrasion of a spiral shaft and a graphite bearing, the maintenance and replacement cost of the spiral shaft is high is solved.

Description

Technical Field

[0001] The utility model relates to the technical field of carbon anode production, and particularly relates to an anti-wear transmission structure at the end of a spiral shaft of a preheater. Background Art

[0002] Preheaters are widely used in the carbon anode production process, especially playing an indispensable role in the preheating stage of carbon anodes. Through its specific design, the preheater can effectively heat the carbon anode to ensure that the carbon anode can reach the required temperature conditions in the subsequent processing, thereby improving its physical properties and chemical stability.

[0003] In the production process of carbon anodes, the preheater is usually located between forming and roasting, and is responsible for preheating the formed carbon anode blanks. Through preheating, the internal stress of the carbon anode is released, and at the same time its organizational structure becomes more uniform, laying a good foundation for the subsequent high-temperature roasting process. The working efficiency and preheating effect of the preheater directly affect the final quality and production efficiency of the carbon anode.

[0004] However, during the actual operation of the preheater, especially in its internal spiral conveying mechanism, the spiral shaft bears the heavy responsibility of material conveying and stirring. Due to the continuous filling of materials inside the box, the spiral shaft bears great resistance and torque during operation. Coupled with its own weight, the graphite bearing at the end of the spiral shaft bears extremely high pressure. This long-term high-load operation leads to an accelerated wear rate of the graphite bearing, seriously affecting the stability and service life of the preheater.

[0005] Once the wear amount of the graphite bearing exceeds its designed thickness, the end of the spiral shaft will come into direct contact with the sealing gland on the side of the graphite bearing. This contact not only exacerbates the wear at the end of the spiral shaft but may also cause the overall sinking of the spiral shaft. The sinking of the spiral shaft will not only cause rubbing against the bottom box but also result in wear of the spiral shaft blades or cracking of the welds, further reducing the working efficiency and safety of the preheater.

[0006] Therefore, it is particularly important to regularly replace and maintain the worn parts of the preheater. However, the process of repairing the wear at the end of the spiral shaft is extremely complex. During the repair process, multiple welding repairs, measurements, and grinding operations are required. At the same time, the welding temperature needs to be strictly controlled to prevent deformation of the end of the spiral shaft. This repair process not only takes a long time but also requires a very high technical level of the operators. If the wear of the spiral shaft is severe enough to cause fracture or weld opening, the entire spiral shaft needs to be replaced. Since the preheater is usually installed on a higher floor, the replacement of the entire spiral shaft requires high-altitude hoisting operations. Such hoisting operations are not only difficult and risky but also have high equipment rental costs, bringing a heavy economic burden to the enterprise. In addition, the procurement cost of replacing the entire spiral shaft is also relatively high, and at the same time, it is necessary to wait for the order period, further extending the downtime of the equipment and increasing the production cost of the enterprise. Summary of the Utility Model

[0007] The present utility model aims to provide an anti-wear drive structure for the end of the spiral shaft of a preheater to solve the technical problem of high maintenance and replacement costs of the spiral shaft caused by the contact wear between the spiral shaft and the graphite bearing in the prior art.

[0008] To achieve the above object, the present utility model adopts the following technical solution: An anti-wear drive structure for the end of the spiral shaft of a preheater, comprising a spiral shaft and a drive mechanism for driving the spiral shaft to rotate. A graphite bearing for supporting the spiral shaft is provided at the end of the spiral shaft. A wear-resistant bushing is arranged between the end of the spiral shaft and the graphite bearing. The wear-resistant bushing is in a cylindrical shape, and a plurality of fixing holes for fixing with the end of the spiral shaft are evenly distributed along the circumferential direction at both ends of the wear-resistant bushing.

[0009] The principle and advantages of this solution are as follows: The wear-resistant bushing is fixedly connected to the end of the spiral shaft through the fixing holes at both ends thereof; when the spiral shaft rotates driven by the drive mechanism, the wear-resistant bushing will rotate together therewith and generate friction with the graphite bearing; the end of the spiral shaft no longer directly contacts the graphite bearing, but rather the graphite bearing generates friction with the wear-resistant bushing; the cost of the wear-resistant bushing is much lower than the replacement cost of the spiral shaft. Therefore, when the wear-resistant bushing is worn to a certain extent, only the wear-resistant bushing needs to be replaced, and there is no need to replace the entire spiral shaft, thus greatly reducing the maintenance cost;

[0010] Replacing the wear-resistant bushing is simpler in operation compared to replacing the entire spiral shaft; there is no need to perform high-altitude hoisting operations or disassemble complex drive mechanisms. Only by loosening the connecting parts in the fixing holes, the wear-resistant bushing can be easily taken out and replaced, greatly reducing the maintenance difficulty and downtime.

[0011] As an improvement, the wear-resistant bushing is a steel bushing. The inner diameter of the wear-resistant bushing is 140 mm, the outer diameter is 160 mm, and the barrel length is 240 mm; the inner diameter of the graphite bearing is 160 mm.

[0012] The beneficial effects of this improvement are as follows: The specific dimension design of the wear-resistant bushing ensures a good fit between it and the end of the spiral shaft and the graphite bearing, guaranteeing the stability of transmission. The steel sleeve, as the material of the wear-resistant bushing, provides sufficient structural strength to withstand the frictional force and torque generated during the rotation of the spiral shaft, further extending the service life.

[0013] As an improvement, a total of 6 fixing holes are provided on the wear-resistant bushing. Three fixing holes are grouped together and evenly arranged circumferentially on the barrel wall of the wear-resistant bushing. The two groups of fixing holes are respectively located at both ends of the wear-resistant bushing and are symmetrically arranged.

[0014] The beneficial effects of this improvement are as follows: The design of 6 fixing holes makes the connection between the wear-resistant bushing and the end of the spiral shaft more stable, avoiding increased wear or transmission failure caused by loose connection; the fixing holes are evenly distributed circumferentially, and the fixing holes at both ends are symmetrically arranged, ensuring uniform force on the wear-resistant bushing during rotation and reducing wear or damage caused by stress concentration.

[0015] As an improvement, 45° chamfers are respectively provided at both ends of the inner side of the wear-resistant bushing.

[0016] The beneficial effects of this improvement are as follows: The design of the 45° chamfer makes it easier for the wear-resistant bushing to align with the end of the spiral shaft during installation, reducing the installation difficulty and time; the presence of the chamfer reduces the stress concentration when the wear-resistant bushing contacts the end of the spiral shaft, further reducing wear and increasing the service life.

[0017] As an improvement, the transmission mechanism includes a motor, a speed reducer, and a transmission gear. The output end of the motor is connected to the input end of the speed reducer, the output end of the speed reducer is connected to the input end of the transmission gear, and the transmission gear is connected to the end of the spiral shaft.

[0018] The beneficial effects of this improvement are as follows: The combined design of the motor, speed reducer, and transmission gear makes the transmission mechanism have higher transmission efficiency and stability, ensuring the smooth rotation of the spiral shaft.

[0019] As an improvement, the spiral shaft includes a dry pipe and spiral blades. The spiral blades are fixedly welded to the outer surface of the dry pipe. Both the spiral blades and the dry pipe are hollow, and the hollow inner cavity of the dry pipe is communicated with the hollow inner cavity of the spiral blades.

[0020] The beneficial effects of this improvement are as follows: It enables the heat transfer medium oil to flow in the dry pipe and spiral blades, increasing the indirect contact area between the heat transfer medium oil and the material and improving the heat dissipation efficiency. Description of the Drawings

[0021] Figure 1 It is a cross-sectional view of the wear-resistant bushing according to the embodiment of the present utility model.

[0022] Figure 2 This is a schematic structural diagram of the wear-resistant bushing in the embodiment of the present utility model.

[0023] Figure 3 This is a cross-sectional view of the spiral shaft in the embodiment of the present utility model.

[0024] Figure 4 This is a cross-sectional view of the rotary joint in the embodiment of the present utility model. Detailed implementation manners

[0025] The following is a further detailed description through specific implementation manners:

[0026] The reference numerals in the accompanying drawings of the specification include: wear-resistant bushing 1, fixed hole 2, oil inlet chamber 3, oil outlet chamber 4, spiral blade 5, surrounding channel 6, main pipe 7, extension pipe 8, housing 9, first bearing 10, second bearing 11, connecting pipe 12, first connecting pipe 13, second connecting pipe 14, oil inlet pipe 15, and oil outlet pipe 16.

[0027] Embodiment

[0028] A preheater with a wear-resistant transmission structure at the end of a spiral shaft includes a box body, a spiral shaft, a transmission mechanism, and a heat-conducting oil inlet and outlet system.

[0029] The box body is welded by steel plates and has sufficient strength and stiffness. The shape of the box body can be a cuboid or a U shape, and the internal space is used to accommodate the spiral shaft and materials. The box body is provided with a feeding port, a discharging port, an observation window, a temperature measuring hole, etc., for operations such as feeding, discharging, observing, and temperature measuring.

[0030] The spiral shaft is made of a hollow steel pipe and is internally provided with a heat-conducting oil channel for introducing high-temperature heat-conducting oil for heating. The outer surface of the spiral shaft is welded with spiral blades 5; the end of the spiral shaft is provided with a graphite bearing and a sealing device for supporting the spiral shaft to ensure stability and sealing during rotation. The spiral shaft is installed inside the box body and maintains a certain gap with the side wall and bottom of the box body. There are four spiral shafts, and the four spiral shafts are horizontally and parallelly installed in the box body for normal rotation and conveying operations. The rotation directions of adjacent spiral shafts are opposite. In this embodiment, the rotation directions of the four spiral shafts from left to right are clockwise, counterclockwise, clockwise, and counterclockwise in sequence.

[0031] The transmission mechanism includes a motor, a speed reducer, and transmission gears. The motor provides the power for the rotation of the screw shaft. The output end of the motor is connected to the input end of the speed reducer, the output end of the speed reducer is connected to the input end of the transmission gears, and the transmission gears are connected to the end of the screw shaft. The speed reducer reduces the speed and increases the torque, and then the power is transmitted to the screw shaft through the transmission gears. The transmission mechanism is installed outside the box body and is located on one side of the end of the screw shaft. The transmission gears of the transmission mechanism are connected to the end of the screw shaft through a coupling or a universal joint, so that the power of the transmission mechanism is transmitted to the screw shaft.

[0032] The heat-conducting oil inlet and outlet system includes heat-conducting oil pipelines, valves, and pumps. The heat-conducting oil pipelines are used to transport high-temperature heat-conducting oil from the heating system to the inside of the screw shaft and the box body, and transport the heat-conducting oil after heat transfer and cooling back to the heating system for reheating. The valves are installed in the heat-conducting oil pipelines to control the flow rate and flow direction of the heat-conducting oil to ensure the stability and safety of the preheating process. The pumps are connected to the heat-conducting oil pipelines to provide the power required for the circulation of the heat-conducting oil. The heat-conducting oil inlet and outlet system is usually installed on the side or bottom of the box body and is connected to the inside of the screw shaft and the box body.

[0033] Due to the filling of materials inside the box body, the screw shaft bears a large amount of resistance and torque during operation. Coupled with its own weight, the wear rate of the graphite bearing at the end of the screw shaft is accelerated. Once the wear amount exceeds the thickness of the graphite bearing, the end of the screw shaft will directly contact the sealing gland on the side of the graphite bearing, which will in turn cause wear at the end of the screw shaft and sinking of the entire screw shaft. This sinking will not only cause rubbing between the screw shaft and the bottom box body, but also cause wear of the screw shaft blades or cracking of the welds. If the wear and sinking problems of the screw shaft are not repaired in time, it will eventually lead to leakage of the heat-conducting oil in the screw shaft or the cavity of the shell 9. Once the heat-conducting oil leaks, it will not only affect the normal operation of the preheater, but also may cause serious consequences such as fires, posing a great threat to production safety and personnel safety.

[0034] The process of repairing the wear at the end of the screw shaft is extremely complex. It is necessary to disassemble multiple key components of the preheater, such as the drive-end motor, speed reducer, gearbox, and graphite bearing seat, etc., and lift the entire screw shaft out of the box body. During the repair process, multiple repairs by welding, measurement, and grinding are also required, and the welding temperature needs to be strictly controlled to prevent deformation of the end of the screw shaft. This repair process not only takes a long time, but also requires extremely high technical levels of the operators. If the screw shaft is severely worn to the extent of fracture or weld opening, the entire screw shaft needs to be replaced. This process not only involves the disassembly and installation of all components of the preheater, but also requires lifting the old shaft from the fifth floor of the high-rise building to the ground and then lifting the new shaft from the ground into the fifth floor. Such lifting operations are not only difficult, but also the equipment rental costs are extremely high, bringing a heavy burden to the production and operation of the enterprise.

[0035] In order to extend the service life of the screw shaft and reduce the maintenance cost of the screw shaft, a wear-resistant sleeve 1 is arranged between the end of the screw shaft and the graphite bearing.

[0036] As attached Figure 1 and attached Figure 2 As shown, the wear-resistant sleeve 1 is cylindrical and is sleeved at the end of the spiral shaft, and is in direct contact with the inner ring of the graphite bearing, so that when the spiral shaft generates rotation resistance, relative friction occurs due to the direct contact between the wear-resistant sleeve 1 and the graphite bearing, thereby avoiding direct wear of the spiral shaft. In addition, during the maintenance of the spiral shaft, only the wear-resistant sleeve 1 and the graphite bearing of the spiral shaft need to be replaced from the outside of the box, which greatly reduces the maintenance time and repair cost.

[0037] The inner diameter of the wear-resistant sleeve 1 is 140mm, the outer diameter is 160mm, and the length of the barrel is 240mm. The wear-resistant sleeve 1 is a steel sleeve, so the size of the original graphite bearing needs to be improved, and the inner diameter of the graphite bearing is changed to 160mm to match the wear-resistant sleeve 1. In order to facilitate the rotation of the sleeve on the spiral shaft, 45° chamfers are set at both ends of the inner side of the wear-resistant sleeve 1 to facilitate the spiral shaft to slide into the wear-resistant sleeve 1. And multiple M8 fixing holes 2 are evenly distributed along the circumference at both ends of the wear-resistant sleeve 1. The M8 fixing holes 2 are internal threaded holes with a thread diameter of 8mm. Six M8 fixing holes 2 are provided on a single wear-resistant sleeve 1, of which three are evenly arranged in a group along the circumference of the barrel wall of the wear-resistant sleeve 1. Two groups of M8 fixing holes 2 are respectively located at both ends of the wear-resistant sleeve 1 and are symmetrically arranged. The screw passes through the M8 fixing hole 2, so that the wear-resistant sleeve 1 and the end of the spiral shaft are tightly fixed to avoid relative friction between the two. When assembling the wear-resistant sleeve 1 and the graphite bearing, heating, tapping and other operations are performed to make the wear-resistant sleeve 1 fit tightly with the inner ring of the graphite bearing.

[0038] In order to increase the heating power of the preheater, the spiral shaft of the preheater is improved:

[0039] As attached Figure 3 As shown, the spiral shaft includes a hollow main pipe 7 and spiral blades 5 fixedly welded to the outside of the main pipe 7;

[0040] A flow channel for the circulation of the heat medium oil is provided in the main pipe 7 , and the flow channel is subdivided into two parts, an oil inlet chamber 3 and an oil outlet chamber 4 , which are arranged adjacent to each other.

[0041] One end of the dry pipe 7 is designed as a through hole arranged along the central axis. This through hole is directly connected to the external heat transfer oil inlet and outlet system to ensure the smooth flow of the heat transfer oil. The other end of the dry pipe 7 is closed so that the heat transfer oil flows in and out of the flow channel on one side of the dry pipe 7, leaving space for the installation of the transmission mechanism, effectively avoiding the mutual interference between the heat transfer oil flow and the transmission mechanism layout.

[0042] The oil inlet chamber 3 is arranged near the closed end of the main pipe 7, and the oil outlet chamber 4 is arranged near the through-port end of the main pipe 7. The through-port of the main pipe 7 is a double-layer pipe orifice. The inner pipe orifice of the through-port is connected to the oil inlet chamber 3 through an extension pipe 8, and the outer pipe orifice of the through-port is connected to the oil outlet chamber 4.

[0043] The spiral blade 5 also adopts a hollow design, and together with the outer surface of the main pipe 7, it forms a surrounding channel 6 for the further circulation and heat dissipation of the heat medium oil. At the position of the oil outlet chamber 4 near the through-port end, a second flow hole communicating with the inner surrounding channel 6 of the spiral blade 5 is provided; while in the oil inlet chamber 3, at the position of the main pipe 7 near the closed end, a first flow hole connecting the oil inlet chamber 3 and the surrounding channel 6 is provided. This design ensures that the heat medium oil can form an effective circulating flow between the main pipe 7 and the spiral blade 5.

[0044] The heat medium oil first passes through the inner pipe orifice, that is, enters the oil inlet chamber 3 through the extension pipe 8, and then flows axially to the first flow hole and enters the surrounding channel 6 of the spiral blade 5. In the surrounding channel 6, the heat medium oil fully releases heat to the materials in the box body to raise the temperature of the materials. After the heat exchange is completed, the heat medium oil with reduced temperature returns to the oil outlet chamber 4 through the second flow hole and finally flows out from the outer pipe orifice and re-enters the heat-conducting oil inlet and outlet system for reheating to form a closed-loop cycle.

[0045] Inside the spiral shaft, the temperature distribution of the heat medium oil shows a gradually decreasing trend from the inside to the outside, ensuring that the heat transfer direction always diffuses outward, maximizing the contact with the materials and improving the heat transfer efficiency. Through the design of the hot oil flow direction, the adverse impact of the heat medium oil that has completed heat dissipation on the temperature of the heat medium oil that is about to perform heat transfer work is effectively avoided, thereby improving the overall heating efficiency.

[0046] An internal thread structure is added to the inner wall of the extension pipe 8. This design guides the hot oil to form a vortex during the rotation of the spiral shaft and the flow of the hot oil, significantly accelerating the flow rate of the hot oil and further improving the heating efficiency.

[0047] Since the external heat-conducting oil inlet and outlet system is fixed, while the spiral shaft rotates during operation, in order to enable the two-state pipe bodies to be connected, a rotary joint is used to connect the through-port of the spiral shaft and the heat-conducting oil inlet and outlet system. To support the requirements of different flow directions on one side of the spiral shaft at the same time (i.e., the double-layer pipe orifice design of the through-port).

[0048] As shown in the Figure 4 appendix, the structure of the rotary joint is specifically as follows:

[0049] The rotary joint includes a housing 9, a first bearing 10 and a second bearing 11. The housing 9 is provided with a first bearing chamber for installing the first bearing 10 and a second bearing chamber for installing the second bearing 11. The first bearing chamber and the second bearing chamber are arranged in sequence along the axial direction of the spiral shaft.

[0050] The main pipe 7 is rotatably connected to the first bearing 10 in the first bearing chamber, and the extension pipe 8 extends out of the main pipe 7 and is rotatably connected to the second bearing 11 in the second bearing chamber.

[0051] The outer ring of the first bearing 10 is fixedly connected to the first bearing chamber. An integrally formed first connecting pipe 13 extending towards the housing 9 is provided on the inner side of the inner ring of the first bearing 10. The first connecting pipe 13 is fixedly connected to the main pipe 7. An adapter pipe 12 closely attached to the inner wall of the first connecting pipe 13 is further provided in the housing 9. One end of the adapter pipe 12 is fixedly connected to the inner surface of the housing 9, and the other end of the adapter pipe 12 extends out of the housing 9 and extends into the inner wall of the main pipe 7. The outer wall of the adapter pipe 12 is closely attached to the inner wall of the main pipe 7. A sealing ring is provided between the adapter pipe 12 and the main pipe 7, and this sealing ring is located at the connection between the main pipe 7 and the first bearing 10. A flange is provided on the outside of the connection between the main pipe 7 and the first bearing 10, and a sealing ring is also provided on the inner side of the flange to wrap the outer surface of the connection between the main pipe 7 and the first bearing 10.

[0052] An oil outlet pipe 16 is provided on the housing 9 between the first bearing chamber and the second bearing chamber. The oil outlet pipe 16 is communicated with the pipeline of the heat-conducting oil inlet and outlet system flowing towards the heating component. An enclosed space for communicating the oil outlet chamber 4 and the oil outlet pipe 16 is formed between the adapter pipe 12 and the extension pipe 8 in the rotary joint.

[0053] The outer ring of the second bearing 11 is fixedly connected to the second bearing chamber. The housing 9 is integrally formed with a second connecting pipe 14 extending towards the first bearing chamber at the position of the second bearing chamber; the inner ring of the second bearing 11 is fixedly connected to the extension pipe 8, and the second connecting pipe 14 is sleeved on the outer wall of the extension pipe 8 and fixedly connected thereto. A sealing ring is provided between the second connecting pipe and the extension pipe 8.

[0054] An oil inlet pipe 15 is provided on the housing 9 along the spiral axis. The oil inlet pipe 15 is communicated with the pipeline of the heat-conducting oil inlet and outlet system flowing out from the heating component. The extension pipe 8 extends into the oil inlet pipe 15 and is closely attached to the oil inlet pipe 15; a sealing ring is further provided between the extension pipe 8 and the oil inlet pipe 15. In this embodiment, the sealing ring is made of a hard-sealed graphite tape fiber component, so that it can withstand a high temperature of 300 degrees Celsius while having good sealing performance.

[0055] In the rotary joint, the extension pipe 8 directly communicates the oil inlet pipe 15 with the oil inlet chamber 3. When the spiral shaft works, the main pipe 7, the extension pipe 8, the inner ring of the first bearing 10, and the inner ring of the second bearing 11 rotate at the same frequency as the spiral shaft. While the housing 9 of the rotary joint, the outer ring of the first bearing 10, the outer ring of the second bearing 11, and the adapter pipe 12 remain stationary, ensuring a stable connection with the external heat-conducting oil inlet and outlet system.

[0056] In the heat-conducting oil inlet and outlet system, the heated hot oil flows into the rotary joint through the inlet pipe 15, and then enters the oil inlet chamber 3 inside the spiral shaft through the extension pipe 8. The cold oil that has completed the heat transfer work inside the spiral shaft flows out through the main pipe 7, enters the outlet pipe 16 through the connecting pipe 12, and finally flows back to the heat-conducting oil inlet and outlet system for reheating.

[0057] The above are only embodiments of the present invention. Specific technical solutions and / or common knowledge such as characteristics known in the art are not described in detail herein. It should be noted that for those skilled in the art, without departing from the technical solution of the present invention, several deformations and improvements can be made, which should also be regarded as the protection scope of the present invention, and these will not affect the implementation effect of the present invention and the practicability of the patent. The protection scope required by this application should be based on the content of its claims, and the specific implementation manners described in the specification can be used to interpret the content of the claims.

Claims

1. A wear-resistant drive structure at the end of the spiral shaft of a preheating machine, characterized in that: It includes a spiral shaft and a transmission mechanism for driving the spiral shaft to rotate. A graphite bearing for supporting the spiral shaft is provided at the end of the spiral shaft. A wear-resistant bushing is arranged between the end of the spiral shaft and the graphite bearing. The wear-resistant bushing is cylindrical. A plurality of fixing holes for fixing with the end of the spiral shaft are evenly distributed along the circumference at both ends of the wear-resistant bushing.

2. The anti-wear transmission structure at the end of the spiral shaft of a preheating machine according to claim 1, characterized in that: The wear-resistant bushing is a steel bushing. The inner diameter of the wear-resistant bushing is 140 mm, the outer diameter is 160 mm, and the barrel length is 240 mm. The inner diameter of the graphite bearing is 160 mm.

3. A wear-resistant drive structure at the end of the spiral shaft of a preheating machine according to claim 2, characterized in that: A total of 6 fixing holes are provided on the wear-resistant bushing. Three fixing holes are in a group and are evenly arranged along the circumference on the barrel wall of the wear-resistant bushing. The two groups of fixing holes are respectively located at both ends of the wear-resistant bushing and are symmetrically arranged.

4. A wear-resistant transmission structure at the end of the spiral shaft of a preheating machine according to claim 3, characterized in that: 45° chamfers are respectively provided at both inner ends of the wear-resistant bushing.

5. A wear-resistant drive structure at the end of the spiral shaft of a preheating machine according to claim 4, characterized in that: The transmission mechanism includes a motor, a reducer and a transmission gear. The output end of the motor is connected to the input end of the reducer, the output end of the reducer is connected to the input end of the transmission gear, and the transmission gear is connected to the end of the spiral shaft.

6. The anti-wear transmission structure at the end of the spiral shaft of a preheating machine according to claim 5, characterized in that: The spiral shaft includes a dry pipe and spiral blades. The spiral blades are fixedly welded on the outer surface of the dry pipe. Both the spiral blades and the dry pipe are hollow. The hollow inner cavity of the dry pipe is communicated with the hollow inner cavity of the spiral blades.

Images