Synthetic ammonia pressure swing adsorption desorption gas treatment centrifugal compressor

Abstract

The utility model provides a synthetic ammonia pressure swing adsorption desorption gas treatment centrifugal compressor which comprises a wheel disc and a centrifugal impeller, wherein the centrifugal impeller is provided with main blades surrounding the outer part of the wheel disc; the overall arrangement mode of the main blades is oblique arrangement, and the starting ends of the main blades incline towards one side, so that the upper half parts of the main blades are configured to be S-shaped. According to the synthetic ammonia pressure swing adsorption desorption gas treatment centrifugal compressor, due to the S-shaped design of the upper half part of the main blade and the accurate layout of the flaring section and the compression section of the compression channel, gas can flow more uniformly and orderly when entering the impeller. This uniformity helps to reduce instability due to flow fluctuations. And due to the design of the flaring section, the gas is properly pre-accelerated and the flow direction is adjusted before entering the compression section. This pre-acceleration contributes to smoothing the gas flow, reducing the impact of the gas on the blades, thereby reducing the risk of surge.

Description

Technical Field

[0001] The utility model relates to the technical field of coal chemical industry synthetic ammonia, in particular to a synthetic ammonia pressure swing adsorption analytical gas processing centrifugal compressor. Background Art

[0002] In the production process of coal chemical synthetic ammonia, pressure swing adsorption devices are widely used to remove carbon dioxide from raw gas to improve the purity and yield of synthetic ammonia. However, this process will produce a large amount of analytical gas, the main components of which include mixed gases such as methane, hydrogen, carbon monoxide and carbon dioxide.

[0003] Traditional treatment methods usually include directly discharging the desorption gas into the atmosphere or passing it into the boiler as fuel gas for combustion. These methods are not only inefficient, but also cause a certain degree of environmental pollution. In particular, due to the variability of the raw gas components, the flow rate of the desorption gas discharged during the pressure swing adsorption process fluctuates greatly. This fluctuation may cause dynamic imbalance of the centrifugal compressor rotor used subsequently, leading to surge. Surge not only reduces the working efficiency of the compressor, but may also damage the equipment and shorten its service life.

[0004] In existing technologies, although some measures have been taken to reduce the impact of flow fluctuations on compressor performance, these measures often have certain limitations. For example, some systems adapt to flow changes by adjusting operating parameters, but this method may not completely eliminate the risk of surge, especially when there is a large deviation in the raw gas composition. In addition, some systems try to stabilize the flow by adding a buffer tank, but this will increase the complexity and cost of the system.

[0005] Therefore, it is necessary to develop a new technical solution to effectively solve the flow fluctuation problem caused by raw gas component deviation. Utility Model Content

[0006] The utility model proposes a centrifugal compressor for processing synthetic ammonia pressure swing adsorption analytical gas, which improves the stability of analytical gas and the operating efficiency of the compressor in the production process of synthetic ammonia in coal chemical industry, while reducing environmental pollution and equipment loss, and solves the problems mentioned in the above background technology.

[0007] The technical solution of the utility model is achieved in this way:

[0008] A centrifugal compressor for treating synthetic ammonia pressure swing adsorption and desorption gas, comprising a centrifugal impeller having a wheel disc and main blades arranged around the wheel disc; the main blades are arranged in an oblique manner, wherein the starting end of the main blade is tilted toward one side, so that the upper half of the main blade is configured in an S shape;

[0009] An airflow channel is separated between adjacent main blades, and the airflow channel is divided into a flaring section, a contracting section and a bursting section by virtue of the S-shaped design of the upper part of the main blade;

[0010] Auxiliary blades are arranged on the wheel disc of the bursting section.

[0011] Furthermore, the starting end of the auxiliary blade is designed to be oblique and smooth.

[0012] Furthermore, the cross-sectional area of ​​the expansion section in the air flow channel changes from large to small.

[0013] Furthermore, the cross-sectional area of ​​the necking section in the air flow channel gradually decreases.

[0014] Furthermore, the cross-sectional area of ​​the burst section in the air flow channel gradually increases.

[0015] Furthermore, it also includes a compressor casing arranged outside the centrifugal impeller.

[0016] Beneficial effects of the technical solution provided by this application:

[0017] The S-shaped design of the upper part of the main blades and the precise layout of the expansion section and compression section of the compression channel of the centrifugal compressor for synthetic ammonia pressure swing adsorption degassing help achieve a more uniform and orderly flow when the gas enters the impeller. This uniformity helps reduce instability caused by flow fluctuations. The design of the expansion section allows the gas to be properly pre-accelerated and the flow direction adjusted before entering the compression section. This pre-acceleration helps smooth the gas flow and reduce the impact of the gas on the blades, thereby reducing the risk of surge. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the embodiments of the utility model 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 utility model. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0019] Figure 1 This is a schematic diagram of a centrifugal compressor for processing gas by pressure swing adsorption of synthetic ammonia according to the utility model;

[0020] Figure 2 This is a schematic diagram of the centrifugal impeller of the utility model;

[0021] Figure 3 It is a schematic diagram of the main blade, auxiliary blade and air flow channel of the utility model.

[0022] In the figure: 100 centrifugal impeller, 110 wheel disc, 120 main blade, 130 auxiliary blade, 140 air flow channel, 141 expansion section, 142 contraction section, 143 burst section; 200 compressor housing. DETAILED DESCRIPTION

[0023] The technical solution of the utility model will be described clearly and completely in conjunction with the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of them. Based on the embodiments of the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0024] Reference Figure 1-3 A centrifugal compressor for treating synthetic ammonia pressure swing adsorption and desorption gas comprises a centrifugal impeller 100 including a wheel disc 110 and main blades 120 arranged around the wheel disc 110; the main blades 120 are arranged in an oblique manner, wherein the starting ends of the main blades 120 are tilted toward one side, so that the upper part of the main blades 120 is configured in an S shape; air flow channels 140 are spaced between adjacent main blades 120, and the air flow channels 140 are differentiated into a flaring section 141, a contracting section 142 and a burst section 143 by virtue of the S-shaped design of the upper part of the main blades 120; and auxiliary blades 130 are arranged on the wheel disc 110 of the burst section 143.

[0025] The wheel disc 110, as the central supporting structure of the centrifugal impeller 100, not only carries the main blades 120 and the auxiliary blades 130, but also bears the centrifugal force generated during high-speed rotation. The design of the wheel disc 110 needs to have sufficient rigidity and strength to ensure stability during the operation of the compressor. The main blades 120 are the main working components for achieving gas compression. They guide the gas to accelerate and increase its pressure inside the centrifugal impeller 100 through specific inclination angles and shape designs. The aerodynamic performance of the main blades 120 directly affects the efficiency and stability of the compressor. The S-shaped design provides a continuously changing airflow channel 140, which helps the gas maintain uniform flow characteristics during acceleration and reduces the generation of airflow separation and turbulence, which is crucial to improving compression efficiency and reducing energy consumption.

[0026] The airflow channel 140 is the path for the gas to flow inside the centrifugal impeller 100. Its design must ensure the continuity and uniformity of the gas flow while reducing the flow resistance and energy loss. The flared section 141 is the entrance area of ​​the airflow channel. Its design helps the gas to gradually accelerate while reducing the disturbance of the gas flow, creating stable conditions for the gas to enter the constricted section 142. The constricted section 142 is the main area of ​​gas compression in the airflow channel. Its design increases the gas velocity, thereby achieving an increase in pressure. This design helps to improve the compression ratio of the compressor. The burst section 143 is the outlet area of ​​the airflow channel. Its design helps to reduce the resistance when the gas is discharged, ensuring that the compressed gas can smoothly enter the next compression stage or discharge the impeller. The auxiliary blade 130 is arranged on the wheel of the burst section 143. Its design helps to stabilize the gas flow, reduce the backflow and vortex of the gas in the burst section 143, and improve the efficiency of gas discharge.

[0027] The following is a further explanation of how the technical features overcome the surge problem mentioned in the background technology:

[0028] The main blades 120 arranged obliquely: help the gas flow more smoothly, reduce the sudden pressure change caused by the gas directly impacting the blades, which is a common cause of surge. The main blades 120 arranged obliquely can distribute the gas flow more effectively and reduce local pressure fluctuations.

[0029] The upper part of the main blade with an S-shaped configuration: The S-shaped design softens the turning of the gas flow and reduces the possibility of gas separation and vortex on the blade surface, which may cause surge in traditional blade designs. The S-shaped design achieves a more gradual speed increase and pressure recovery by extending the gas flow path.

[0030] Precise layout of the expansion section 141, the constriction section 142 and the burst section 143: The continuous design of the expansion section 141, the constriction section 142 and the burst section 143 provides a gradual compression process, avoiding abrupt changes in the gas flow, which is another common cause of surge. The decreasing cross-sectional area of ​​the expansion section 141 helps the gas accelerate smoothly, the gradually decreasing cross-sectional area of ​​the constriction section 142 helps control the compression rate, and the gradually increasing cross-sectional area of ​​the burst section 143 helps to smoothly release the compressed energy.

[0031] The oblique and smooth design of the auxiliary blade 130: The oblique and smooth design of the auxiliary blade 130 helps to reduce the disturbance and backflow of the gas flow in the burst section, which may cause surge at the edge of the impeller. The auxiliary blade 130 reduces the dynamic load of the gas on the impeller by smoothly guiding the gas flow, thereby reducing the risk of surge.

[0032] The entire impeller maintains a better dynamic balance when rotating at high speeds through the coordinated design of the S-shaped main blades 120 and the auxiliary blades 130. This balance reduces vibrations caused by mass imbalance or gas dynamics, which are the direct cause of surge.

[0033] Working principle details:

[0034] Gas introduction: Gas enters from the suction port of the compressor, first contacts the outside of the centrifugal impeller 100, and begins to flow in the air flow channel 140 inside the impeller.

[0035] Gas pre-acceleration and direction adjustment: The gas enters the expansion section 141 , where the cross-sectional area of ​​the airflow channel 140 is designed so that the gas begins to accelerate and adjusts the flow direction under the guidance of the main blades 141 , preparing to enter the compression section 142 .

[0036] Gas compression process: When the gas flows through the constricted section 142, the cross-sectional area of ​​the gas flow channel 140 is further reduced, resulting in an increase in gas velocity. According to the Bernoulli principle, the gas pressure increases accordingly, achieving compression.

[0037] Gas kinetic energy conversion: In the burst section 143, the cross-sectional area of ​​the air flow channel increases, the gas velocity reaches the maximum, the kinetic energy increases, and it is ready to be discharged from the impeller.

[0038] Gas discharge and the role of the auxiliary blade 130: The compressed gas is discharged in the burst section 143, and the oblique and smooth design of the auxiliary blade 130 helps to guide the gas to discharge smoothly and reduce energy loss during the discharge process.

[0039] Reduced surge risk: The S-shaped design of the main blade 120, the precise segmentation of the airflow channel 140, and the optimized design of the auxiliary blade 130 work together to reduce the impact of flow fluctuations on compressor performance and reduce the risk of surge. The optimized gas flow path and compression process reduce energy loss and improve the operating efficiency of the compressor. At the same time, by reducing the surge phenomenon, the stability and reliability of the equipment are improved.

[0040] In some embodiments, the starting end of the auxiliary blade 130 is designed to be oblique and smooth.

[0041] The oblique and smooth design of the auxiliary blades 130 reduces the disturbance of the gas flow when approaching the burst section 143. This disturbance may cause unstable gas flow in traditional designs, thereby causing surge. The oblique design reduces this instability by providing a smoother flow transition. In the burst section 143, the gas velocity is extremely high. If the flow is not properly controlled, it may cause gas backflow and form surge. The oblique design of the auxiliary blades 130 helps to guide the gas to discharge smoothly, reduce the backflow phenomenon, and thus reduce the risk of surge. The oblique design of the beginning of the auxiliary blades 130 improves the dynamic characteristics of the gas in the burst section 143 and reduces the dynamic pressure fluctuations of the gas in high-speed rotation. These fluctuations are one of the important reasons for the occurrence of surge. The optimized design of the auxiliary blades 130 reduces the surge-induced stress on the impeller structure, thereby reducing the risk of structural fatigue and damage and extending the service life of the equipment.

[0042] In some embodiments, the cross-sectional area of ​​the expansion section 141 in the air flow channel 140 decreases from large to small.

[0043] The design of the cross-sectional area of ​​the expanded section 141 gradually decreases so that the gas can be accelerated gradually when entering the impeller, rather than suddenly. This gradual acceleration helps to reduce shocks and sudden pressure changes in the gas flow. By controlling the cross-sectional area of ​​the gas flow passage to gradually decrease, the expanded section 141 helps to maintain the stability of the gas flow and avoid gas flow separation and vortex caused by sudden changes in the cross-sectional area. The gradual decrease in the cross-sectional area of ​​the expanded section 141 helps to improve compression efficiency because it allows the gas to reach an appropriate speed before entering the compression section 142, thereby compressing more efficiently.

[0044] In some embodiments, the cross-sectional area of ​​the narrowed section 142 in the air flow channel 140 gradually decreases.

[0045] The constricted section 142 controls the compression rate of the gas by gradually reducing the cross-sectional area, thus avoiding a sudden change in pressure caused by the gas being compressed too quickly. The design of gradually reducing the cross-sectional area helps to form an appropriate pressure gradient in the constricted section 142, making the increase in gas pressure more uniform and controllable, and reducing the possibility of surge. By precisely controlling the shape of the airflow channel, the constricted section 142 reduces the separation phenomenon in the gas flow. Flow separation will form vortices on the blade surface, increasing the risk of surge.

[0046] In some embodiments, the cross-sectional area of ​​the burst section 143 in the air flow channel 140 gradually increases.

[0047] The cross-sectional area of ​​the burst section 143 gradually increases, which helps to alleviate the surge caused by the rapid release of gas pressure. This design allows the gas to have a gradual decompression process before it is discharged from the impeller. The design of the burst section 143 reduces the possibility of gas backflow near the discharge port, which may interfere with the stable flow of the impeller. As the cross-sectional area increases, the resistance encountered by the gas during the discharge process decreases, reducing the surge caused by the sudden change of discharge resistance.

[0048] In some embodiments, a compressor housing 200 is further included which is arranged outside the centrifugal impeller 100 .

[0049] The compressor housing 200 provides a solid structural support for the centrifugal impeller 100 and other internal components, ensuring mechanical stability during the operation of the compressor. The housing 200 defines the outer boundary of the gas flow, guiding the gas to enter the next process stage or the exhaust system after being discharged from the impeller. By working in conjunction with the impeller 100, the housing 200 helps maintain a certain pressure level inside the compressor, providing the necessary pressure environment for gas compression and flow.

[0050] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A centrifugal compressor for treating synthetic ammonia pressure swing adsorption and desorption gas, comprising a wheel disc (110) and a centrifugal impeller (100) with main blades (120) arranged around the wheel disc (110); characterized in that: The main blade (120) is disposed in an oblique manner as a whole, wherein the starting end of the main blade (120) is tilted toward one side, so that the upper half of the main blade (120) is configured in an S shape; An airflow channel (140) is formed between adjacent main blades (120), and the airflow channel (140) is divided into an expansion section (141), a contraction section (142) and a burst section (143) by virtue of the S-shaped design of the upper part of the main blade (120); Auxiliary blades (130) are provided on the wheel disc (110) of the burst section (143).

2. The centrifugal compressor for treating synthetic ammonia pressure swing adsorption and desorption gas according to claim 1, characterized in that: The starting end of the auxiliary blade (130) is designed to be oblique and smooth.

3. The centrifugal compressor for treating synthetic ammonia pressure swing adsorption and desorption gas according to claim 1, characterized in that: The cross-sectional area of ​​the expanded section (141) in the airflow channel (140) changes from large to small.

4. The centrifugal compressor for treating synthetic ammonia pressure swing adsorption and desorption gas according to claim 1, characterized in that: The cross-sectional area of ​​the narrowing section (142) in the air flow channel (140) gradually decreases.

5. The centrifugal compressor for treating synthetic ammonia pressure swing adsorption and desorption gas according to claim 1, characterized in that: The cross-sectional area of ​​the burst section (143) in the air flow channel (140) gradually increases.

6. The centrifugal compressor for treating synthetic ammonia pressure swing adsorption and desorption gas according to claim 1, characterized in that: It also includes a compressor housing (200) arranged outside the centrifugal impeller (100).

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