Energy-saving pure oxygen three-section centrifugal compressor

Abstract

The invention provides an energy-saving type pure oxygen three-section centrifugal compressor, and relates to the technical field of energy-saving type gas compressors, the energy-saving type pure oxygen three-section centrifugal compressor comprises a gearbox, a driving shaft, a bearing, an impeller and a volute set, the volute set is communicated with a cooling system through a cold air inlet, the impeller and the driving shaft are coaxially arranged, and the impeller and the driving shaft are connected with an annular volute cavity through an air supply flow channel; and a diffuser is arranged in the air supply flow channel. The compressor is provided with a split flow channel, a first oil storage mechanism, a pneumatic oil guide mechanism and a second oil storage mechanism, the split flow channel is connected with a diffuser and a bearing rolling gap, and the pneumatic oil guide mechanism is used for controlling lubricating oil supply of the first oil storage mechanism, opening a lubricating oil channel under the action of wind power and automatically closing when no wind power exists. The precise conveying and efficient utilization of the lubricating oil are achieved, the lubricating effect is improved, the consumption of the lubricating oil is reduced, and compared with the prior art, the energy consumption problem caused by intermittent starting and stopping can be greatly reduced.

Description

Technical Field

[0001] The invention relates to the technical field of energy-saving gas compressors, and in particular to an energy-saving pure oxygen three-stage centrifugal compressor. Background Art

[0002] At present, the compression and delivery of high-purity oxygen is one of the key technical links in the fields of industrial production, aerospace, medical treatment and diving. Pure oxygen compressors mainly use piston or centrifugal compression methods. Among them, centrifugal compressors are widely used in high-purity oxygen compression applications due to their compact structure, stable operation, and suitability for large flow conditions.

[0003] In the prior art, common pure oxygen centrifugal compressors usually adopt a multi-stage compression structure. For example, patent document CN201916218U discloses a geared air compressor for a PTA device, which includes multiple impellers arranged in series. Each stage of the impeller increases the oxygen pressure through a diffuser, and a cooling device is provided between the stages to reduce the temperature rise of the oxygen, thereby improving the compression efficiency. This solution can meet the pure oxygen compression requirements to a certain extent and has been applied in some industrial fields.

[0004] However, although the existing multi-stage compression and interstage cooling technologies can meet the needs of pure oxygen compression to a certain extent, there are still certain technical limitations. Specifically, although the interstage cooling device can reduce the temperature rise of oxygen, in actual operation, the rotating parts of the compressor, including the rotating contact area between the rotor (gear shaft) corresponding to each stage of the impeller and the compressor casing, often generate high temperatures due to long-term operation, and the existing technology does not provide effective cooling measures for this part. Therefore, when the compressor continues to operate under high temperature load conditions, the temperature of the rotating parts may rise rapidly and eventually exceed the safety threshold, causing the equipment to have to stop running for cooling and then restart. This intermittent start-stop mode not only affects the continuous operation of the equipment, but also causes additional energy waste, which limits the energy efficiency performance of existing pure oxygen centrifugal compressors in high temperature environments.

[0005] Therefore, how to ensure high-purity oxygen compression performance while effectively reducing the temperature rise of rotating parts during compressor operation, thereby improving the continuous working ability and overall energy efficiency of the equipment, has become an urgent problem to be solved in the current technical field. Summary of the invention

[0006] The present application discloses an energy-saving pure oxygen three-stage centrifugal compressor to solve the technical problem of serious energy consumption of pure oxygen centrifugal compressors in related technologies.

[0007] The present application provides an energy-saving pure oxygen three-stage centrifugal compressor, which adopts the following technical solution: An energy-saving pure oxygen three-stage centrifugal compressor comprises a gearbox, a driving shaft, a bearing, an impeller and a volute group. The volute group is provided with three groups on the outer wall of the gearbox, and each group of the volute group is connected with the cooling system through a cold air inlet. The driving shaft is rotatably arranged on the gearbox through a bearing, and the impeller is coaxially arranged at one end of the driving shaft located outside the gearbox; the volute group comprises a volute casing, a shaped ring and a diffuser. The volute casing is fixedly arranged on the outer wall of the gearbox, the shaped ring is arranged in the volute casing, the impeller is in the shaped ring, and the outer wheel wall of the impeller and the inner wall of the shaped ring form an air supply channel, and the diffuser is communicated and arranged at the connection between the air supply channel and the annular volute cavity; it also comprises a split flow channel, a first oil storage mechanism, a pneumatic oil introduction mechanism and a second oil storage mechanism. The split flow channel is arranged between the gearbox and the volute group, and the split One end of the flow channel is connected to the inside of the diffuser, and the other end is directed to the rolling gap of the bearing. The first oil storage mechanism is arranged on the gear box and connected to the split flow channel. The pneumatic oil introduction mechanism is arranged at the connection between the first oil storage mechanism and the split flow channel. The second oil storage mechanism is arranged on the gear box and is located directly below the bearing. The pneumatic oil introduction mechanism has a switchable first state and a second state. When there is wind flow in the split flow channel, the pneumatic oil introduction mechanism switches to the first state under the action of wind and opens the connection between the first oil storage mechanism and the split flow channel, so that the lubricating oil in the first oil storage mechanism follows the wind flow to the rolling gap of the bearing; when there is no wind flow in the split flow channel, the pneumatic oil introduction mechanism automatically maintains the second state and closes the connection between the first oil storage mechanism and the split flow channel.

[0008] Preferably, the split flow channel includes a guide segment, a drainage segment and an oil and gas output segment which are connected in sequence, wherein one end of the guide segment away from the drainage segment is connected to the inside of the diffuser; the aperture of the drainage segment gradually decreases from one end close to the guide segment to one end close to the oil and gas output segment; one end of the oil and gas output segment away from the drainage segment is opposite to the rolling clearance of the bearing, and the first oil storage mechanism is arranged above the oil and gas output segment and is connected to the oil and gas output segment.

[0009] Preferably, the first oil storage mechanism includes a first oil storage tank, a temporary oil storage tank and an oil storage membrane body, the first oil storage tank is detachably arranged above the temporary oil storage tank, and the lower end of the temporary oil storage tank is connected to the drainage segment; the oil storage membrane body includes an adhesive membrane segment and a hollow membrane segment, the adhesive membrane segment is bonded to the inner wall of the temporary oil storage tank, one end of the hollow membrane segment is connected to the adhesive membrane segment, and the other end is connected to the inner wall of the temporary oil storage tank to form an oil storage space for storing lubricating oil, and the lubricating oil flowing into the oil storage membrane body from the first oil storage tank is directly collected in the oil storage space.

[0010] Preferably, the pneumatic oil induction mechanism includes a rotating component and an opening and closing component, wherein the rotating component is rotatably arranged at the connection point between the temporary oil storage tank and the drainage segment, and the rotating component blocks most of the flow cross-section of the drainage segment when in a natural state; an oil outlet is provided on the side wall of the temporary oil storage tank away from the rotating component, the oil storage space is connected with the oil and gas output segment through the oil outlet, and the opening and closing component is rotatably arranged on the side wall of the temporary oil storage tank away from the rotating component and is used to block the oil outlet; when there is wind flow in the split flow channel, the part of the rotating component affected by the wind moves away from the flow cross-section of the drainage segment, so as to synchronously drive the opening and closing component to move away from the position blocking the oil outlet, and the pneumatic oil induction mechanism is in a first state at this time; when there is no wind flow in the split flow channel, the rotating component is reset to a position blocking most of the flow cross-section of the drainage segment in a natural state, and at the same time, the opening and closing component is reset to a position blocking the oil outlet, and the pneumatic oil induction mechanism is in a second state.

[0011] Preferably, the rotating assembly includes a first torsion spring and a rotating block, the cross-sectional shape of the rotating block is fan-shaped, and the tip of the rotating block is rotatably connected to the inner wall of one side of the temporary oil storage tank; the first torsion spring is arranged at the rotating connection between the rotating block and the temporary oil storage tank, the rotating block has a windward surface and a pushing surface that are opposite to each other, and the first torsion spring always has a tendency to push the windward surface to the flow path of the drainage segment.

[0012] Preferably, the opening and closing assembly includes an L-shaped baffle and a second torsion spring, the corner of the L-shaped baffle is rotatably connected to the inner wall of the other side of the temporary oil storage tank, the second torsion spring is arranged at the rotational connection between the L-shaped baffle and the temporary oil storage tank, one side baffle portion of the L-shaped baffle overlaps the pushing surface, the other side baffle of the L-shaped baffle is used to block the oil outlet, and the second torsion spring always has a tendency to push the L-shaped baffle to block the oil outlet; the rotating block is located outside the oil storage space, and the L-shaped baffle is located inside the oil storage space, so that when one side baffle portion of the L-shaped baffle overlaps the pushing surface, the hollow membrane segment is clamped between the two.

[0013] Preferably, an arc-shaped bending section is also provided on one side of the lower opening of the temporary oil storage tank, and one end of the hollow membrane section away from the adhesion membrane section is connected to the arc-shaped bending section, and an avoidance gap is formed above the arc-shaped bending section so that the other side of the L-shaped baffle can rotate normally within the avoidance gap.

[0014] Preferably, the oil outlet is connected to an oil outlet flow channel, and the oil storage space is connected to the oil and gas output section through the oil outlet flow channel; the height of the end of the oil outlet flow channel close to the oil outlet is higher than the height of the end close to the oil and gas output flow channel, and the inner diameter of the oil outlet flow channel gradually increases from the end of the oil outlet flow channel close to the oil outlet to the end of the oil outlet flow channel close to the oil and gas output flow channel.

[0015] Preferably, a drainage limit portion is provided on the lower inner wall of the connection between the drainage section and the oil and gas output section, and the drainage limit portion has a guide surface and an anti-backflow surface, the guide surface is inclined toward the drainage section, and the anti-backflow surface is inclined toward the oil and gas output section, wherein; along the flow direction of the wind force, the guide surface is inclined and smoothly extends upward, and the anti-backflow surface is inclined and smoothly extends downward, and the guide surface and the anti-backflow surface are smoothly transitioned and connected.

[0016] Preferably, the second oil storage mechanism includes an arcuate oil guide groove body and a second oil storage tank. The arcuate oil guide groove body is installed on the bottom wall of the gear box and is located directly below the bearing to receive excess lubricating oil flowing out of the rolling clearance of the bearing. The second oil storage tank is detachably arranged at the lowest end of the arcuate oil guide groove body so that the lubricating oil collected in the arcuate oil guide groove body can flow to the second storage tank for storage under the action of gravity.

[0017] The present invention has the following advantages and beneficial effects: 1. The present invention optimizes the storage and recovery of lubricating oil by setting a first oil storage mechanism and a second oil storage mechanism, so that the lubricating oil can be fully utilized during the operation of the equipment. Among them, the first oil storage mechanism adopts the design of an oil storage film body, so that the lubricating oil can be stored in a centralized manner, reducing the risk of leakage, and the lubricating oil is transported to the rolling gap of the bearing when needed through a pneumatic oil guide mechanism, thereby improving the delivery efficiency of the lubricating oil. At the same time, the second oil storage mechanism uses an arc-shaped oil guide groove body and a detachable second oil storage tank to allow the lubricating oil overflowing from the bearing to flow smoothly and be recovered into the oil storage tank, thereby avoiding disorderly diffusion or waste of the lubricating oil. In addition, the inclined design of the oil outlet flow channel and the structure with a gradually increasing inner diameter help to control the flow rate and flow of the lubricating oil, so that it can be transported and recovered within a reasonable range, thereby reducing the waste caused by insufficient or excessive supply of lubricating oil. Through this series of optimization measures, the present invention can improve the recycling rate of lubricating oil to a certain extent, reduce maintenance costs, reduce the consumption of lubricating oil, and reduce environmental pollution problems that may occur during the operation of the equipment; 2. The present invention adopts a pneumatic oil introduction mechanism, and realizes the precise delivery of lubricating oil through the synergistic effect of the rotating component and the opening and closing component. When there is wind flow in the drainage segment, the rotating component rotates under the action of the wind, so that the opening and closing component synchronously moves the oil outlet, allowing the lubricating oil to flow into the oil and gas output segment, and then enter the rolling gap of the bearing. When there is no wind flow in the split flow channel, the rotating component and the opening and closing component are reset under the elastic force of the torsion spring, blocking the oil outlet, preventing the lubricating oil from entering the bearing at unnecessary times, thereby reducing unnecessary consumption of lubricating oil. This design combines the elastic force of the first torsion spring and the second torsion spring, so that the pneumatic oil introduction mechanism can automatically switch states under different working conditions without the need for additional electrical control or mechanical drive, thereby simplifying the structure and improving the reliability of the system. In addition, the design of the oil storage membrane body and its hollow membrane segment helps to maintain the stable storage state of the lubricating oil and reduce the loss or volatilization of the lubricating oil due to external factors. Through the above-mentioned optimized design, the present invention can achieve accurate delivery of lubricating oil to a certain extent, which helps to improve the lubrication conditions of the bearing, reduce the discharge of excess lubricating oil, and improve the operating stability of the equipment; 3. In order to further optimize the flow path of the lubricating oil, the present invention designs a drainage limiter at the connection between the drainage segment and the oil and gas output segment. The limiter is composed of a guide surface and an anti-backflow surface, and the two are connected by a smooth transition. In the direction of wind flow, the guide surface extends upward and tilts, which helps to guide the lubricating oil to flow to the oil and gas output segment along a predetermined path, while the anti-backflow surface extends downward and tilts, which can effectively prevent the lubricating oil from flowing back, so that the lubricating oil can be more stably delivered to the rolling gap of the bearing. In addition, the inner diameter of the oil outlet flow channel gradually increases along the delivery direction. This gradually expanding structure can reduce the flow resistance, so that the lubricating oil can enter the oil and gas output segment more smoothly, avoiding the problem of flow obstruction or blockage. Through these optimized designs, the present invention reduces the fluctuations in the lubricating oil delivery process to a certain extent, makes the oil supply of the lubrication system more stable, reduces the abnormal wear of the bearing caused by uneven lubricating oil supply or obstructed flow, thereby extending the service life of the equipment and improving the reliability and safety of operation. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0019] Figure 1 It is a partial schematic diagram used to demonstrate the energy-saving pure oxygen three-stage centrifugal compressor in the embodiment of the present application; Figure 2It is a schematic diagram for showing the positional relationship among the split flow channel, the first oil storage mechanism, the pneumatic oil introduction mechanism and the second oil storage mechanism in the embodiment of the present application; Figure 3 yes Figure 2 Enlarged view of part A in .

[0020] The markings in the figure are: 1. Gearbox; 11. Drive shaft; 12. Bearing; 13. Impeller; 14. Cold air inlet; 2. Volute assembly; 21. Volute casing; 211. Annular volute cavity; 22. Shaped ring; 23. Diffuser; 24. Air supply channel; 3. Split flow channel; 31. Diversion segment; 32. Diversion segment; 33. Oil and gas output segment; 4. First oil storage mechanism; 41. First oil storage tank; 42. Temporary oil storage tank; 421. Oil outlet; 43. Oil storage membrane; 431. Adhesion membrane segment; 432. hollow membrane section; 44. oil storage space; 5. pneumatic oil introduction mechanism; 51. rotating assembly; 511. first torsion spring; 512. rotating block; 5121. windward surface; 5122. pushing surface; 52. opening and closing assembly; 521. L-shaped baffle; 522. second torsion spring; 6. second oil storage mechanism; 61. arc-shaped oil guide groove body; 62. second oil storage tank; 7. arc-shaped bending section; 8. oil outlet channel; 9. drainage limiter; 91. guiding surface; 92. anti-backflow surface. DETAILED DESCRIPTION

[0021] To make the purpose, technical solution and advantages of the present invention clearer, the technical solution of the present invention will be described in detail below. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other implementation methods obtained by ordinary technicians in this field without creative work belong to the scope of protection of the present invention.

[0022] The terms "first", "second", etc. in the specification and claims of the present application are used to distinguish similar objects, and are not used to describe a specific order or sequence. It should be understood that the data used in this way can be interchangeable under appropriate circumstances, so that the embodiments of the present application can be implemented in an order other than those illustrated or described here, and the objects distinguished by "first", "second", etc. are generally of one type, and the number of objects is not limited. For example, the first object can be one or more. In addition, "and / or" in the specification and claims represents at least one of the connected objects, and the character " / " generally indicates that the objects associated with each other are in an "or" relationship.

[0023] The present invention is further described in detail below in conjunction with the accompanying drawings. Figure 1 to Figure 3The present application provides an energy-saving pure oxygen three-stage centrifugal compressor. The compressor comprises a gearbox 1, a driving shaft 11, a bearing 12, an impeller 13 and a volute group 2, wherein the volute group 2 is arranged on the outer wall of the gearbox 1 in three groups, each group of the volute group 2 is connected to the external cooling system through a cold air inlet 14, so that the cold air can enter the air supply channel 24, the driving shaft 11 is rotatably arranged on the gearbox 1 through the bearing 12, and the impeller 13 is coaxially arranged at one end of the driving shaft 11 outside the gearbox 1.

[0024] Exemplarily, the volute group 2 includes a volute casing 21, a g-shaped ring 22 and a diffuser 23. The volute casing 21 is fixed to the outer wall of the gearbox 1, and the g-shaped ring 22 is arranged in the volute casing 21. The volute casing 21 is provided with an annular volute cavity 211 on the outer periphery of the g-shaped ring 22. The impeller 13 is in the g-shaped ring 22, and the outer wheel wall of the impeller 13 and the inner wall of the g-shaped ring 22 form an air supply channel 24. One end of the air supply channel 24 is connected to the cooling system and the other end is connected to the annular volute cavity 211. The aperture of the air supply channel 24 gradually decreases from one end to the other end, and the diffuser 23 is connected at the connection between the air supply channel 24 and the annular volute cavity 211.

[0025] Exemplarily, the compressor also includes a split flow channel 3, a first oil storage mechanism 4, a pneumatic oil induction mechanism 5 and a second oil storage mechanism 6. The split flow channel 3 is arranged between the gear box 1 and the volute group 2, and one end of the split flow channel 3 is connected to the inside of the diffuser 23, and the other end is facing the rolling gap of the bearing 12. The first oil storage mechanism 4 is arranged on the gear box 1 and connected to the split flow channel 3. The pneumatic oil induction mechanism 5 is arranged at the connection between the first oil storage mechanism 4 and the split flow channel 3. The second oil storage mechanism 6 is arranged on the gear box 1 and is located directly below the bearing 12. The pneumatic oil induction mechanism 5 has a switchable first state and a second state.

[0026] Illustratively, when there is wind flow in the split flow channel 3, the pneumatic oil induction mechanism 5 switches to the first state under the action of the wind and opens the connection between the first oil storage mechanism 4 and the split flow channel 3, so that the lubricating oil in the first oil storage mechanism 4 flows into the rolling gap of the bearing 12 following the wind.

[0027] Exemplarily, when there is no wind flow in the split flow channel 3 , the pneumatic oil introduction mechanism 5 automatically maintains the second state and closes the connection between the first oil storage mechanism 4 and the split flow channel 3 .

[0028] On this basis, the air supply channel 24 is designed as a structure with a gradually decreasing aperture, so that the cold air is gradually pressurized during the flow process, increasing the flow rate and enhancing the cooling effect. The pressurized cold air is further pressurized in the diffuser 23 and then enters the annular volute cavity 211, and then enters the next stage compression unit through the volute group 2. This cycle is repeated three times, which can effectively reduce the temperature rise of oxygen and improve the overall compression efficiency of the compressor.

[0029] In addition, when the cold air flows through the diffuser 23, part of the cold air will be introduced into the split flow channel 3, which is arranged between the gear box 1 and the volute assembly 2, so that the cold air can be blown directly to the rolling gap of the bearing 12, thereby cooling the bearing 12. Since the bearing 12 is subjected to a high rotational load during the operation of the compressor, its rolling gap is easily heated by friction, and with the help of the cold air flow in the split flow channel 3, the temperature of the bearing 12 can be reduced to a certain extent, thereby improving the working stability of the bearing 12. At the same time, the cold air flow in the split flow channel 3 can also synchronously drive the pneumatic oil introduction mechanism 5, which is arranged between the first oil storage mechanism 4 and the split flow channel 3, and can be switched to the first state under the action of wind, so that the lubricating oil in the first oil storage mechanism 4 is introduced into the split flow channel 3, and enters the rolling gap of the bearing 12 with the cold air, providing lubrication for the bearing 12. The entry of lubricating oil not only reduces the friction at the rolling gap of the bearing 12, helping to reduce the wear of the bearing 12, but also can further absorb the heat of the bearing 12. When the lubricating oil flows out of the rolling gap and enters the second oil storage mechanism 6, part of the heat is also taken away, so that the overall temperature of the bearing 12 can be controlled.

[0030] This design means that when the compressor is running at high load, there is no need to frequently stop to cool the bearing 12. Instead, it can maintain normal operation while using the cold air originally used for oxygen cooling to simultaneously achieve bearing 12 cooling and lubricating oil supply, thereby reducing the start-stop loss of the compressor, improving the continuous operation capability of the equipment, and reducing the overall energy consumption to a certain extent.

[0031] In addition, when there is no wind flowing in the split flow channel 3, the pneumatic oil introduction mechanism 5 will automatically maintain the second state, preventing the lubricating oil from continuing to flow into the rolling clearance of the bearing 12, so as to avoid uneven lubrication or other operating problems that may be caused by excessive entry of lubricating oil. Therefore, this design takes into account the balance between cooling, lubrication and operating stability.

[0032] In summary, the present invention not only improves the oxygen compression efficiency of the pure oxygen centrifugal compressor by optimizing the cold air path design, but also provides an efficient solution for the temperature control and lubrication management of the bearing 12, so that the equipment can operate stably for a long time and reduce the possibility of energy waste and operation interruption caused by high temperature shutdown.

[0033] In some embodiments, in combination Figure 1 to Figure 3In order to optimize the cold air flow path and improve the cooling effect on the bearing 12, the split flow channel 3 includes a guide segment 31, a drainage segment 32 and an oil and gas output segment 33 which are connected in sequence, wherein the end of the guide segment 31 away from the drainage segment 32 is connected to the inside of the diffuser 23; the aperture of the drainage segment 32 gradually decreases from the end close to the guide segment 31 to the end close to the oil and gas output segment 33; illustratively, the end of the oil and gas output segment 33 away from the drainage segment 32 is opposite to the rolling clearance of the bearing 12, and the first oil storage mechanism 4 is arranged above the oil and gas output segment 33 and is connected to the oil and gas output segment 33.

[0034] Exemplarily, the flow guiding segment 31 and the flow diversion segment 32 are connected by an arc-shaped smooth transition.

[0035] On this basis, the inlet of the guide segment 31 is far away from one end of the diversion segment 32 and is directly connected to the inside of the diffuser 23, so that the cold air from the diffuser 23 can smoothly enter the split flow channel 3. In order to reduce the pressure loss of the cold air during the flow process, the guide segment 31 and the diversion segment 32 are connected by an arc-shaped smooth transition. This structure can make the cold air less affected by sudden resistance when flowing through this area, thereby maintaining a relatively stable pressure effect and improving the continuity and uniformity of the cold air flow. When the cold air enters the diversion segment 32, since the aperture of the segment gradually decreases from the end close to the guide segment 31 to the end close to the oil and gas output segment 33, the cold air will be further pressurized in this area due to the contraction of the flow channel, increasing the flow speed and power of the cold air, making the subsequent wind force sprayed to the rolling gap of the bearing 12 stronger, and the cooling effect on the bearing 12 is more obvious. Finally, the pressurized cold air flows out from the oil and gas output segment 33, and the outlet of the oil and gas output segment 33 faces the rolling gap of the bearing 12, so that the cold air can directly act on the bearing 12 to improve the cooling efficiency. In addition, the first oil storage mechanism 4 is arranged above the oil and gas output segment 33 and is connected to the oil and gas output segment 33. This structure helps when the pneumatic oil introduction mechanism 5 is switched to the first state, so that the lubricating oil can enter the oil and gas output segment 33 along with the cold air, and be transported to the rolling gap of the bearing 12 along with the airflow to achieve the lubrication function. Through the above structural design, not only can the cold air be pressurized twice before entering the bearing 12, thereby improving the cooling effect, but it can also ensure that the delivery of the lubricating oil matches the flow of the cold air, so that the bearing 12 can be cooled and lubricated more stably under high temperature operating conditions, which is beneficial to improving the reliability and energy efficiency of the centrifugal compressor during continuous operation.

[0036] In some embodiments, in combination Figure 1 to Figure 3In order to optimize the storage and delivery structure of the lubricating oil and improve the storage stability of the lubricating oil, the first oil storage mechanism 4 is designed to include a first oil storage tank 41, a temporary oil storage tank 42 and an oil storage membrane 43. The first oil storage tank 41 is detachably arranged above the temporary oil storage tank 42, and the lower end of the temporary oil storage tank 42 is connected to the drainage segment 32. Exemplarily, an internally threaded pipe is arranged at the lower end of the first oil storage tank 41, and an externally threaded pipe is arranged above the temporary oil storage tank 42, and the internally threaded pipe and the externally threaded pipe are threadedly connected to realize the detachable connection between the two. Further, other detachable methods, such as snap-on connection, etc., can also be used.

[0037] Exemplarily, the oil storage film body 43 includes an adhesive film segment 431 and a hollow film segment 432, the adhesive film segment 431 is bonded to the inner wall of the temporary oil storage tank 42, and one end of the hollow film segment 432 is connected to the adhesive film segment 431 and the other end is connected to the inner wall of the temporary oil storage tank 42 to form an oil storage space 44 for storing lubricating oil, and the lubricating oil flowing into the oil storage film body 43 from the first oil storage tank 41 is directly collected in the oil storage space 44.

[0038] Exemplarily, the oil storage film body 43 is made of PTFE film or PET composite film.

[0039] On this basis, the oil storage film body 43 allows the lubricating oil flowing from the first oil storage tank 41 to be directly collected in the oil storage space 44, and due to the wrapping effect of the oil storage film body 43, the risk of lubricating oil leakage is reduced to a certain extent, and the storage stability of the lubricating oil is improved. At the same time, the existence of the oil storage film body 43 can also play a certain buffering role on the lubricating oil, so that it maintains a good uniformity during storage and flow, which is beneficial to the subsequent stable delivery of the lubricating oil, so that the lubricating oil can enter the rolling clearance of the bearing 12 more evenly, improve the lubrication effect and cooling effect of the bearing 12, and extend the service life of the compressor bearing 12 to a certain extent.

[0040] In some embodiments, in combination Figure 1 to Figure 3 The pneumatic oil induction mechanism 5 includes a rotating component 51 and an opening and closing component 52, wherein the rotating component 51 is rotatably arranged at the connection point between the temporary oil storage tank 42 and the drainage segment 32, and the rotating component 51 blocks most of the flow cross-section of the drainage segment 32 when in a natural state.

[0041] Exemplarily, an oil outlet 421 is provided on the side wall of the temporary oil storage tank 42 away from the rotating component 51, the oil storage space 44 is connected with the oil and gas output section 33 through the oil outlet 421, and the opening and closing component 52 is rotatably arranged on the side wall of the temporary oil storage tank 42 away from the rotating component 51 and is used to block the oil outlet 421.

[0042] Illustratively, when there is wind flow in the split flow channel 3, the part of the rotating component 51 affected by the wind moves away from the flow section of the diversion segment 32, so as to synchronously drive the opening and closing component 52 to move away from the position blocking the oil outlet 421. At this time, the pneumatic oil diversion mechanism 5 is in the first state.

[0043] Furthermore, when there is no wind flow in the split flow channel 3, the rotating component 51 is naturally reset to a position that blocks most of the flow cross-section of the diversion segment 32, and at the same time, the opening and closing component 52 is reset to a position that blocks the oil outlet 421. At this time, the dynamic oil diversion mechanism is in the second state.

[0044] On this basis, when cold wind flows in the split flow channel 3, the airflow of the cold wind will generate a certain thrust on the rotating component 51, so that the rotating component 51 is forced to rotate, thereby partially removing the obstruction of the flow cross section of the drainage segment 32, and then the cold wind can smoothly enter the oil and gas output segment 33. At the same time, the rotation of the rotating component 51 will also synchronously drive the movement of the opening and closing component 52, specifically: when the rotating component 51 is rotated by the wind force, the opening and closing component 52 will be synchronously pulled, thereby moving away from the position of blocking the oil outlet 421, so that the lubricating oil can smoothly flow from the oil storage space 44 through the oil outlet 421 into the oil and gas output segment 33, and finally be transported to the rolling gap of the bearing 12 together with the cold wind to achieve lubrication and cooling.

[0045] On the contrary, when the flow of cold air in the split flow channel 3 stops, the rotating component 51 loses the effect of wind force and will naturally reset to the position of blocking the flow section of the drainage segment 32, while driving the opening and closing component 52 to synchronously reset to the position of blocking the oil outlet 421, so that the lubricating oil stops flowing out. Through such a design, the timing of releasing the lubricating oil can match the flow state of the cold air, and the lubricating oil is only released when the cold air flows. On the one hand, this can ensure that the lubricating oil always flows with the cold air to the rolling gap of the bearing 12, improving the lubrication and cooling effect, and on the other hand, it also reduces the ineffective consumption of lubricating oil, making the use of lubricating oil more efficient.

[0046] In some embodiments, in combination Figure 1 to Figure 3In order to make the release timing of the lubricating oil accurately match the flow state of the cold wind, and quickly block the oil outlet 421 when the cold wind stops flowing, the pneumatic oil introduction mechanism 5 further optimizes the structure of the rotating component 51 and the opening and closing component 52, so that it can respond to wind force changes more efficiently. Further, the rotating component 51 includes a first torsion spring 511 and a rotating block 512. The cross-sectional shape of the rotating block 512 is fan-shaped, and the tip of the rotating block 512 is rotatably connected to the inner wall of one side of the temporary oil storage tank 42. Exemplarily, the first torsion spring 511 is arranged at the rotation connection between the rotating block 512 and the temporary oil storage tank 42. The rotating block 512 has a windward surface 5121 and a pushing surface 5122 that are separated from each other. The first torsion spring 511 always has a tendency to push the windward surface 5121 to the flow path of the drainage segment 32, so that when there is no wind force, the rotating block 512 naturally returns to the state of blocking the flow path.

[0047] In some embodiments, in combination Figure 1 to Figure 3 The opening and closing assembly 52 includes an L-shaped baffle 521 and a second torsion spring 522. The corner of the L-shaped baffle 521 is rotatably connected to the inner wall of the other side of the temporary oil storage tank 42. The second torsion spring 522 is arranged at the rotation connection between the L-shaped baffle 521 and the temporary oil storage tank 42. The side edge of the L-shaped baffle 521 overlaps the push surface 5122. The side edge of the L-shaped baffle 521 is used to block the oil outlet 421. The second torsion spring 522 always has a tendency to push the L-shaped baffle 521 to block the oil outlet 421. Exemplarily, the rotating block 512 is located outside the oil storage space 44, and the L-shaped baffle 521 is located inside the oil storage space 44, so that when the side edge of the L-shaped baffle 521 overlaps the push surface 5122, the hollow film segment 432 is sandwiched between the two.

[0048] Such a design allows the movement of the rotating block 512 to directly affect the state of the L-shaped baffle 521, thereby achieving a synchronous opening and closing effect driven by wind. Specifically, when cold air flows in the drainage segment 32, since the cold air has been pressurized twice after passing through the design of the aforementioned diversion segment 31 and the drainage segment 32, its energy is relatively large and can directly act on the windward surface 5121, causing the windward surface 5121 to rotate after being impacted, so that the entire rotating block 512 is lifted under the action of wind. As the rotating block 512 is lifted, its push surface 5122 synchronously drives one side of the L-shaped baffle 521 to lift. At this time, the other side of the baffle that blocks the oil outlet 421 will gradually move away from the oil outlet 421, thereby opening the oil outlet 421, so that the lubricating oil can smoothly enter the oil and gas output segment 33 from the oil storage space 44 through the oil outlet 421, and be transported to the rolling gap of the bearing 12 driven by wind, completing the lubrication and cooling process. It is worth noting that the rotating block 512 is made of lightweight material and is relatively light in weight, and the impact force of the twice-pressurized cold air can completely lift the rotating block 512 .

[0049] When the flow of cold air in the drainage segment 32 stops, the rotating block 512, which has lost its wind support, will quickly reset to a position that blocks most of the flow cross section of the drainage segment 32 under the combined action of the elastic force of the first torsion spring 511 and its own gravity. At the same time, since one side of the L-shaped baffle 521 is still overlapped on the push surface 5122 of the rotating block 512, when the rotating block 512 is reset, the L-shaped baffle 521 will also be synchronously reset to a position that blocks the oil outlet 421 under the torsion of the second torsion spring 522, so that the flow of lubricating oil stops, avoiding the situation where lubricating oil still flows out after the compressor is shut down. In this way, the structure can not only ensure that the lubricating oil is released only when needed, improve the efficiency of the use of lubricating oil, but also reduce unnecessary consumption of lubricating oil, making the replenishment cycle of lubricating oil longer. At the same time, the structure can reduce the malfunction caused by wind fluctuations to a certain extent, improve the stability of the lubrication system, and enable it to maintain a good lubrication effect under different operating conditions.

[0050] In some embodiments, in combination Figure 1 to Figure 3 The lower opening side of the temporary oil storage tank 42 is also provided with an arc-shaped bending section 7, and the end of the hollow film section 432 away from the adhesion film section 431 is connected to the arc-shaped bending section 7, and an escape gap is formed above the arc-shaped bending section 7, so that the other side of the L-shaped baffle 521 can rotate normally within the escape gap. Exemplarily, the bending arc of the arc-shaped bending section 7 is adapted to the rotation arc of the other side of the L-shaped baffle 521. Exemplarily, the arc-shaped bending section 7 and the oil and gas output section 43 are also smoothly transitioned, so that the cold air is not easily lost when passing through here.

[0051] After such arrangement, the arc-shaped bending section 7 forms a certain avoidance gap above it, providing sufficient movement space for the other side guard of the L-shaped baffle 521, thereby ensuring that the L-shaped baffle 521 can smoothly rotate around the rotating part without being blocked or interfered by the oil storage film body 43. In particular, when the L-shaped baffle 521 is opened by the wind to open the oil outlet 421, the guard of the other side will move along a fixed trajectory. If there is no avoidance gap, it may come into contact with the oil storage film body 43, causing the oil storage film body 43 to be scratched or even damaged. By setting the arc-shaped bending section 7 and forming the avoidance gap, the L-shaped baffle 521 is always in a reasonable range of movement during the entire rotation process, reducing the friction contact with the oil storage film body 43, which is beneficial to extend the service life of the oil storage film body 43 to a certain extent. In addition, the bending structure of the arc-shaped bending section 7 itself can also play a certain role in fixing and supporting the hollow film section 432, preventing it from deforming or shifting when subjected to force, thereby further improving the stability of the oil storage film body 43 and making the storage and release process of the lubricating oil more reliable.

[0052] In summary, this structural design not only optimizes the movement trajectory of the L-shaped baffle 521, enabling it to complete the opening and closing action more smoothly, but also reduces the loss of the oil storage film body 43, thereby improving the durability and working stability of the entire oil storage mechanism.

[0053] In some embodiments, in combination Figure 1 to Figure 3 The oil outlet 421 is connected to an oil outlet channel 8, and the oil storage space 44 is connected to the oil and gas output segment 33 through the oil outlet channel 8; illustratively, the height of the end of the oil outlet channel 8 close to the oil outlet 421 is higher than the height of the end close to the oil and gas output channel, and the inner diameter of the oil outlet channel 8 gradually increases from the end of the oil outlet channel 8 close to the oil outlet 421 to the end of the oil outlet channel 8 close to the oil and gas output channel.

[0054] On this basis, the design of the oil outlet flow channel 8 takes into account the gravity and pressure difference factors of fluid transportation. The height of the end close to the oil outlet 421 is higher than the height of the end close to the oil and gas output flow channel, so as to form a certain potential energy difference by utilizing the height difference, which helps the lubricating oil flow along the flow channel to the oil and gas output segment 33. In addition, in order to reduce the flow resistance and improve the stability of the oil flow, the inner diameter of the oil outlet flow channel 8 gradually increases from the end close to the oil outlet 421 to the end close to the oil and gas output flow channel. Such a structural design reduces the fluid flow resistance in the flow channel to a certain extent, so that the lubricating oil can be more smoothly transported to the oil and gas output segment 33 during the flow process, and is also conducive to reducing the oil accumulation phenomenon that may occur in the flow channel when the lubricating oil flow rate is small. Since the inner diameter of the oil outlet flow channel 8 gradually increases, the lubricating oil can be properly diffused during the flow process, so that it is more evenly distributed when it is transported to the oil and gas output segment 33, the utilization efficiency of the lubricating oil is improved, and a more stable lubrication effect is provided to key parts such as the bearing 12.

[0055] In some embodiments, in combination Figure 1 to Figure 3 In order to optimize the flow path of cold air and lubricating oil, and to reduce the backflow of lubricating oil caused by air flow disturbance to a certain extent, a diversion limiting portion 9 is provided on the lower inner wall of the connection between the diversion segment 32 and the oil and gas output segment 33. The diversion limiting portion 9 includes a guide surface 91 and an anti-backflow surface 92, wherein the guide surface 91 is inclined toward the diversion segment 32, and extends smoothly upward along the flow direction of the wind force, so that the airflow can be gradually guided into the oil and gas output segment 33 along its inclined direction when flowing through the guide surface 91, thereby reducing turbulence and improving flow stability. At the same time, the anti-backflow surface 92 is inclined toward the oil and gas output segment 33, and extends smoothly downward along the flow direction of the wind force, so that the cold air and lubricating oil will not easily flow back to the diversion segment 32 after flowing into the oil and gas output segment 33, thereby optimizing the delivery path of the lubricating oil and reducing the problem of lubricating oil accumulation or poor flow caused by air flow backflow.

[0056] In addition, the guide surface 91 and the anti-backflow surface 92 are connected in a smooth transition manner, making the flow of cold air and lubricating oil smoother, avoiding the increase of fluid disturbance due to sudden structural changes, thereby affecting the stable delivery of lubricating oil. In general, this structural design improves the delivery efficiency of cold air and lubricating oil by optimizing the fluid flow path, while reducing the risk of backflow of lubricating oil to a certain extent, thereby improving the stability of compressor operation and the reliability of the lubrication system.

[0057] In some embodiments, in combination Figure 1 to Figure 3 In order to reasonably recover and temporarily store the lubricating oil overflowing from the rolling clearance of the bearing 12 and improve the utilization rate of the lubrication system, a second oil storage mechanism 6 is provided. The second oil storage mechanism 6 includes an arc-shaped oil guide groove body 61 and a second oil storage tank 62, wherein the arc-shaped oil guide groove body 61 is fixedly mounted on the bottom wall of the gear box 1 and arranged directly below the bearing 12 to receive the excess lubricating oil overflowing from the rolling clearance of the bearing 12.

[0058] On this basis, the structure of the arc-shaped oil guide groove body 61 is designed in a certain arc shape, so that the lubricating oil can naturally gather to the lowest point along the arc surface under the action of gravity, thereby reducing the retention of lubricating oil in the groove body and improving the collection efficiency of lubricating oil. At the same time, a detachable second oil storage tank 62 is provided at the lowest end of the arc-shaped oil guide groove body 61 to store the lubricating oil collected in the oil guide groove body, so that the lubricating oil can be temporarily stored in a centralized manner before being further used, avoiding the normal operation of the compressor due to excessive accumulation. In addition, since the second oil storage tank 62 adopts a detachable design, it can be easily operated when it needs to be replaced or cleaned, which improves the convenience of maintenance. The design of this structure is beneficial to reducing the waste of lubricating oil to a certain extent, while optimizing the recycling of the lubrication system and improving the operating stability and service life of the equipment.

[0059] Exemplarily, the second oil storage tank 62 is of the same model as the first oil storage tank 41. Thus, after there is no lubricating oil in the first oil storage tank 41 and the second oil storage tank 62 is filled with sufficient lubricating oil, the positions of the two can be swapped, so that the lubricating oil can be reused and the replacement is more convenient and quick.

[0060] The above are only specific embodiments of the present invention, but the protection scope of the present invention is not limited thereto. Any technician familiar with the technical field can easily think of changes or substitutions within the technical scope disclosed by the present invention, which should be covered by the protection scope of the present invention.

Claims

1. An energy-saving pure oxygen three-stage centrifugal compressor, characterized in that: The invention comprises a gearbox (1), a driving shaft (11), a bearing (12), an impeller (13) and a volute group (2), wherein three groups of volute groups (2) are arranged on the outer wall of the gearbox (1), each group of volute groups (2) is connected to a cooling system via a cold air inlet (14), the driving shaft (11) is rotatably arranged on the gearbox (1) via a bearing (12), and the impeller (13) is coaxially arranged at one end of the driving shaft (11) located outside the gearbox (1); The volute assembly (2) comprises a volute casing (21), a ring (22) and a diffuser (23); the volute casing (21) is fixedly mounted on the outer wall of the gear box (1); the ring (22) is disposed in the volute casing (21); the impeller (13) is disposed in the ring (22); the outer wheel wall of the impeller (13) and the inner wall of the ring (22) form an air supply channel (24); and the diffuser (23) is disposed in communication at the connection between the air supply channel (24) and the annular volute cavity (211); The invention also comprises a split flow passage (3), a first oil storage mechanism (4), a pneumatic oil introduction mechanism (5) and a second oil storage mechanism (6); the split flow passage (3) is arranged between the gear box (1) and the volute assembly (2); one end of the split flow passage (3) is connected to the inside of the diffuser (23), and the other end faces the rolling gap of the bearing (12); the first oil storage mechanism (4) is arranged on the gear box (1) and is connected to the split flow passage (3); the pneumatic oil introduction mechanism (5) is arranged at the connection point between the first oil storage mechanism (4) and the split flow passage (3); the second oil storage mechanism (6) is arranged on the gear box (1) and is located directly below the bearing (12); the pneumatic oil introduction mechanism (5) has a switchable first state and a second state, wherein: When wind flows in the split flow channel (3), the pneumatic oil introduction mechanism (5) switches to the first state under the action of the wind and opens the connection between the first oil storage mechanism (4) and the split flow channel (3), so that the lubricating oil in the first oil storage mechanism (4) flows into the rolling gap of the bearing (12) following the wind; When there is no wind flow in the split flow channel (3), the pneumatic oil introduction mechanism (5) automatically maintains the second state and closes the connection between the first oil storage mechanism (4) and the split flow channel (3).

2. The energy-saving pure oxygen three-stage centrifugal compressor according to claim 1 is characterized in that: The split flow channel (3) comprises a flow guide segment (31), a flow diversion segment (32) and an oil and gas output segment (33) which are connected in sequence, wherein: One end of the flow guiding segment (31) away from the flow guiding segment (32) is in communication with the interior of the diffuser (23); The aperture of the flow diversion segment (32) gradually decreases from an end close to the flow diversion segment (31) to an end close to the oil and gas output segment (33); One end of the oil and gas output section (33) away from the drainage section (32) faces the rolling clearance of the bearing (12), and the first oil storage mechanism (4) is arranged above the oil and gas output section (33) and is connected to the oil and gas output section (33).

3. The energy-saving pure oxygen three-stage centrifugal compressor according to claim 2 is characterized in that: The first oil storage mechanism (4) comprises a first oil storage tank (41), a temporary oil storage tank (42) and an oil storage membrane (43); the first oil storage tank (41) is detachably arranged above the temporary oil storage tank (42); the lower end of the temporary oil storage tank (42) is connected to the drainage segment (32); The oil storage film body (43) comprises an adhesive film segment (431) and a hollow film segment (432); the adhesive film segment (431) is bonded to the inner wall of the temporary oil storage tank (42); one end of the hollow film segment (432) is connected to the adhesive film segment (431) and the other end is connected to the inner wall of the temporary oil storage tank (42), so as to form an oil storage space (44) for storing lubricating oil, and the lubricating oil flowing from the first oil storage tank (41) into the oil storage film body (43) is directly collected in the oil storage space (44).

4. The energy-saving pure oxygen three-stage centrifugal compressor according to claim 3 is characterized in that: The pneumatic oil-introducing mechanism (5) comprises a rotating component (51) and an opening and closing component (52), wherein: The rotating assembly (51) is rotatably arranged at the connection point between the temporary oil storage tank (42) and the drainage segment (32), and the rotating assembly (51) blocks most of the flow cross section of the drainage segment (32) in a natural state; An oil outlet (421) is provided on a side wall of the temporary oil storage tank (42) away from the rotating assembly (51); the oil storage space (44) is connected to the oil and gas output section (33) via the oil outlet (421); and the opening and closing assembly (52) is rotatably disposed on a side wall of the temporary oil storage tank (42) away from the rotating assembly (51) and is used to block the oil outlet (421); When wind flows in the split flow channel (3), the portion of the rotating component (51) affected by the wind moves away from the flow cross section of the diversion segment (32), thereby synchronously driving the opening and closing component (52) to move away from the position where the oil outlet (421) is blocked. At this time, the pneumatic oil diversion mechanism (5) is in the first state; When there is no wind flow in the split flow channel (3), the rotating component (51) is reset in a natural state to a position where a large portion of the flow cross section of the diversion segment (32) is blocked, and at the same time, the opening and closing component (52) is reset to a position where the oil outlet (421) is blocked. At this time, the dynamic oil diversion mechanism is in the second state.

5. The energy-saving pure oxygen three-stage centrifugal compressor according to claim 4 is characterized in that: The rotating assembly (51) comprises a first torsion spring (511) and a rotating block (512); the rotating block (512) has a fan-shaped cross section, and the tip of the rotating block (512) is rotatably connected to an inner wall of one side of the temporary oil storage tank (42); The first torsion spring (511) is arranged at the rotation connection between the rotating block (512) and the temporary oil storage tank (42); the rotating block (512) has a windward surface (5121) and a pushing surface (5122) that are separated from each other; and the first torsion spring (511) always has a tendency to push the windward surface (5121) onto the flow path of the drainage segment (32).

6. The energy-saving pure oxygen three-stage centrifugal compressor according to claim 5, characterized in that: The opening and closing assembly (52) comprises an L-shaped baffle (521) and a second torsion spring (522); the corner of the L-shaped baffle (521) is rotatably connected to the inner wall of the other side of the temporary oil storage tank (42); the second torsion spring (522) is arranged at the rotatable connection between the L-shaped baffle (521) and the temporary oil storage tank (42); a side rib of the L-shaped baffle (521) overlaps the pushing surface (5122); the other side rib of the L-shaped baffle (521) is used to block the oil outlet (421); and the second torsion spring (522) always has a tendency to push the L-shaped baffle (521) to block the oil outlet (421); The rotating block (512) is located outside the oil storage space (44), and the L-shaped baffle plate (521) is located inside the oil storage space (44), so that when a side baffle portion of the L-shaped baffle plate (521) overlaps the pushing surface (5122), the hollow film segment (432) is sandwiched between the two.

7. The energy-saving pure oxygen three-stage centrifugal compressor according to claim 6, characterized in that: An arc-shaped bending section (7) is further provided on one side of the lower opening of the temporary oil storage tank (42); one end of the hollow film section (432) away from the adhesion film section (431) is connected to the arc-shaped bending section (7); and an escape gap is formed above the arc-shaped bending section (7) so that the other side guard of the L-shaped baffle (521) can rotate normally within the escape gap.

8. The energy-saving pure oxygen three-stage centrifugal compressor according to claim 7, characterized in that: The oil outlet (421) is connected to an oil outlet passage (8), and the oil storage space (44) is connected to the oil and gas output section (33) through the oil outlet passage (8); The height of one end of the oil outlet flow channel (8) close to the oil outlet (421) is higher than the height of one end close to the oil and gas output flow channel, and the inner diameter of the oil outlet flow channel (8) gradually increases from one end of the oil outlet flow channel (8) close to the oil outlet (421) to one end of the oil outlet flow channel (8) close to the oil and gas output flow channel.

9. The energy-saving pure oxygen three-stage centrifugal compressor according to claim 8, characterized in that: A flow limiting portion (9) is provided on the lower inner wall of the connection between the flow guiding section (32) and the oil and gas output section (33), the flow limiting portion (9) having a guide surface (91) and an anti-backflow surface (92), the guide surface (91) being inclined toward the flow guiding section (32), and the anti-backflow surface (92) being inclined toward the oil and gas output section (33); wherein: Along the flow direction of the wind force, the guide surface (91) extends smoothly upwardly at an inclination, the backflow prevention surface (92) extends smoothly downwardly at an inclination, and the guide surface (91) and the backflow prevention surface (92) are connected in a smooth transition.

10. An energy-saving pure oxygen three-stage centrifugal compressor according to any one of claims 1 to 9, characterized in that: The second oil storage mechanism (6) comprises an arc-shaped oil guide groove body (61) and a second oil storage tank (62). The arc-shaped oil guide groove body (61) is mounted on the bottom wall of the gear box (1) and is located directly below the bearing (12) to receive excess lubricating oil flowing out of the rolling clearance of the bearing (12). The second oil storage tank (62) is detachably arranged at the lowest end of the arc-shaped oil guide groove body (61) so that the lubricating oil collected in the arc-shaped oil guide groove body (61) flows to the second storage tank under the action of gravity for storage.

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