Large centrifugal compressor

Abstract

The utility model provides a large-sized centrifugal compressor which comprises a shell assembly, a compressor assembly, a compressor assembly, a compressor assembly and a compressor assembly, and the shell assembly is provided with a gas channel in the axial direction of the shell assembly; the main shaft is arranged in the gas channel, and impeller sets are arranged on the main shaft in the radial direction of the main shaft at intervals; wherein a heat preservation layer is arranged on the outer side of the shell. The heat preservation layer is arranged on the outer side of the shell assembly, so that the compressor has good heat insulation performance, heat exchange between the compressor and the external environment in the running process of the compressor can be effectively reduced, energy loss is reduced, and the recovery and storage efficiency of heat generated in the working process of the compressor is improved; the bearing sealing piece is arranged in the air inlet side bearing box, so that external leakage of gas and internal leakage of oil gas are avoided, and the use safety is improved.

Description

Technical Field

[0001] This application belongs to the field of compressor technology, specifically relating to a large centrifugal compressor. Background Technology

[0002] Compressed air energy storage is a highly efficient energy storage method. Its principle involves using electricity to drive a compressor via an electric motor, compressing air into high-pressure gas and storing it in a storage tank. Alternatively, high-pressure air can be cryogenically liquefied and stored in a tank. When energy is needed, compressed air is released from the storage tank, or liquefied air is vaporized and used to drive a generator via an expander to produce electricity.

[0003] During the compression stage, an electric motor-driven compressor draws in atmospheric air and mechanically compresses it into a high-pressure gas of 70–200 atmospheres, which is then injected into the gas storage tank. In addition to storing pressure energy, the heat energy generated during compression is recovered and stored in oil or molten salt. However, existing compressors have poor insulation, resulting in significant energy loss. Utility Model Content

[0004] This utility model aims to solve at least one of the technical problems existing in the prior art or related technologies.

[0005] To address the aforementioned problems, this application provides a large centrifugal compressor, comprising:

[0006] A housing assembly having a gas passage along its axial direction;

[0007] A main shaft is disposed within the gas passage, and impeller groups are spaced apart along its radial direction on the main shaft;

[0008] An insulation layer is provided on the outer side of the shell.

[0009] Optionally, the housing assembly includes:

[0010] An air intake housing, wherein an air intake port is provided at the first end of the air intake housing;

[0011] A pressure-bearing housing, the first end of which is connected to the second end of the air intake housing, and the second end of the pressure-bearing housing is provided with an exhaust port;

[0012] The insulation layer is disposed on the outside of the air intake shell and the pressure-bearing shell.

[0013] Optionally, an intake-side bearing housing is provided inside the intake housing, and the first end of the main shaft is located inside the intake-side bearing housing. A support bearing and a bearing seal are provided between the intake-side bearing housing and the main shaft.

[0014] Optionally, a stiffening rib is provided between the intake-side bearing housing and the intake casing.

[0015] Optionally, an exhaust-side bearing housing is provided on one side of the pressure-bearing housing, and a thrust bearing is provided inside the exhaust-side bearing housing. The second end of the main shaft is connected to the thrust bearing.

[0016] Optionally, a shaft end seal and a balance disc are provided inside the pressure-bearing housing and between it and the main shaft.

[0017] Optionally, the impeller assembly includes a first impeller, a second impeller, a third impeller, and a fourth impeller sequentially disposed on the main shaft, wherein the flow coefficient of the first impeller is between 0.16 and 0.25.

[0018] Optionally, a partition is provided on the main shaft and located between the first impeller, the second impeller, the third impeller and the fourth impeller.

[0019] Optionally, an adjustable guide vane is provided inside the air intake housing, and the adjustable guide vane is located between the air intake side bearing housing and the first impeller.

[0020] Optionally, a driver is provided outside the air intake housing to drive the adjustable guide vane to rotate. The driver includes a bevel gear and a gear ring. The bevel gear is connected to the adjustable guide vane, and the gear ring is meshed with the bevel gear.

[0021] Beneficial effects

[0022] The large centrifugal compressor provided in the embodiments of this utility model has good heat insulation performance by setting a heat insulation layer on the outside of the shell assembly, which can effectively reduce the heat exchange between the compressor and the external environment during operation, reduce energy loss, and improve the efficiency of heat recovery and storage generated during compressor operation; by setting the bearing seal in the bearing box on the intake side, gas leakage and oil leakage are avoided, thus improving the safety of use. Attached Figure Description

[0023] Figure 1 This is a front view structural diagram of the large centrifugal compressor of this utility model;

[0024] Figure 2 This is an enlarged structural diagram of the air inlet casing of the large centrifugal compressor of this utility model;

[0025] Figure 3 This is an enlarged structural diagram of the pressure-bearing housing of the large centrifugal compressor of this utility model;

[0026] Figure 4 This is a structural diagram of the adjustable guide vane of the large centrifugal compressor of this utility model.

[0027] The reference numerals in the attached figures are as follows:

[0028] 1. Casing assembly; 2. Main shaft; 3. Insulation layer; 4. Inlet casing; 5. Pressure bearing casing; 6. Inlet side bearing housing; 7. Support bearing; 8. Bearing seal; 9. Rib plate; 10. Exhaust side bearing housing; 11. Thrust bearing; 12. Shaft end seal; 13. Balance disc; 14. First impeller; 15. Second impeller; 16. Third impeller; 17. Fourth impeller; 18. Partition plate; 19. Adjustable guide vane; 20. Bevel gear; 21. Gear ring. Detailed Implementation

[0029] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0030] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, "a plurality of" means two or more, unless otherwise explicitly specified.

[0031] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0032] The preferred embodiments of the present invention will be described below with reference to the accompanying drawings. It should be understood that the preferred embodiments described herein are for illustration and explanation only and are not intended to limit the present invention.

[0033] See also Figure 1-4 As shown, an embodiment of this application provides a large centrifugal compressor, comprising:

[0034] Housing assembly 1, wherein a gas passage is provided along its axial direction;

[0035] Main shaft 2, the main shaft 2 is disposed in the gas channel, and impeller groups are spaced apart on the main shaft 2 along its radial direction;

[0036] The outer side of the shell is provided with a heat insulation layer 3.

[0037] In this embodiment, the large centrifugal compressor includes a housing assembly 1, a main shaft 2, an impeller assembly, and an insulation layer 3. The housing assembly 1 is the load-bearing structure of the entire compressor, and its axially oriented gas passage provides a specific spatial path for gas flow and compression. The housing is made of high-strength and high-temperature resistant alloy materials, such as specially formulated chromium-molybdenum alloy steel, to ensure good structural stability and sealing performance under high-pressure gas and long-term operation.

[0038] The main shaft 2, located within the gas passage, serves as the core component driving the impeller assembly's rotation. It is forged from high-strength, high-quality alloy steel and undergoes rigorous heat treatment and precision machining processes to ensure extremely high strength, rigidity, and balance accuracy. The surface of the main shaft 2 undergoes a special hardening treatment to enhance its wear resistance and fatigue resistance, enabling long-term stable operation under high-speed rotation. Impeller assemblies are arranged radially at intervals on the main shaft 2. The impellers are made of high-strength alloy steel. The blade shape and angle of the impellers are set according to usage requirements to ensure effective transfer of mechanical energy to the gas during rotation, achieving efficient gas compression. The gas enters the impeller along the axial direction, reducing inlet chamber losses.

[0039] The outer shell is wrapped with a 60mm-80mm thick insulation layer 3, which has good thermal insulation performance, effectively reducing heat exchange between the compressor and the external environment during operation, reducing energy loss, and improving the efficiency of heat recovery and storage generated during compressor operation.

[0040] Meanwhile, the insulation layer 3 not only helps maintain the temperature stability of the gas inside the compressor and improves compression efficiency, but also reduces the risk of burns to operators due to contact with the high-temperature shell, while reducing energy consumption.

[0041] The housing assembly 1 includes:

[0042] Air intake housing 4, wherein an air intake port is provided at the first end of the air intake housing 4;

[0043] The pressure-bearing housing 5 has a first end connected to the second end of the air intake housing 4, and the second end of the pressure-bearing housing 5 is provided with an exhaust port.

[0044] The insulation layer 3 is disposed on the outside of the air intake shell 4 and the pressure-bearing shell 5.

[0045] In this embodiment, the housing assembly 1 includes an intake housing 4 and a pressure-bearing housing 5 connected thereto. The intake housing 4 includes an upper intake housing and a lower intake housing, and the pressure-bearing housing 5 includes an upper pressure-bearing housing and a lower pressure-bearing housing. The upper intake housing and the lower intake housing are connected to form the intake housing 4, and the upper pressure-bearing housing and the lower pressure-bearing housing are connected to form the pressure-bearing housing 5, which realizes the assembly of the compressor and facilitates the installation of components such as the main shaft 2 during the assembly process. The insulation layer 3 is wrapped around the outside of the intake housing 4 and the pressure-bearing housing 5 to reduce energy loss during operation and improve the efficiency of heat recovery and storage generated during the operation of the compressor.

[0046] An intake-side bearing housing 6 is provided inside the intake housing 4. The first end of the main shaft 2 is located inside the intake-side bearing housing 6. A support bearing 7 and a bearing seal 8 are provided between the intake-side bearing housing 6 and the main shaft 2.

[0047] In this embodiment, an intake-side bearing housing 6 is provided inside the intake housing 4. The intake-side bearing housing 6 and the lower intake housing are cast as a single unit, improving the stability of the connection and eliminating the need for subsequent installation, thus increasing its strength. The first end of the main shaft 2 is located inside the intake-side bearing housing 6, which provides stable support and positioning for the first end of the main shaft 2. A support bearing 7 and a bearing seal 8 are provided between the intake-side bearing housing 6 and the main shaft 2. The support bearing 7 is a high-precision, high-load-bearing rolling bearing, such as an angular contact ball bearing or a tapered roller bearing, with the specific type selected according to the stress and speed requirements of the main shaft 2. It provides stable radial and axial support to the main shaft 2, reducing vibration and wear and ensuring smooth operation of the compressor. The bearing seal 8 prevents lubricating oil leakage from the bearing housing and also prevents external dust and impurities from entering the bearing housing and affecting the normal operation of the bearing. Furthermore, by placing the bearing seal 8 inside the intake-side bearing housing 6, external gas leakage and internal oil leakage are avoided, improving safety during use.

[0048] In actual operation, gas enters the compressor through the inlet housing 4, and the main shaft 2 drives the impeller assembly to rotate at high speed. During rotation, the impellers perform work on the gas through the blades, increasing the gas's speed and pressure. After continuous compression by multiple impeller stages, the gas pressure gradually increases until it reaches the required pressure value and is discharged from the compressor. The support bearing 7 and bearing seal 8 in the inlet-side bearing housing 6 work together to ensure the stable operation of the main shaft 2.

[0049] A stiffening plate 9 is provided between the air intake side bearing housing 6 and the air intake housing 4.

[0050] In this embodiment, the stiffener 9 is installed between the intake side bearing housing 6 and the intake housing 4. The stiffener 9 is used to support and fix the intake side bearing housing 9, thereby improving the stability of the intake side bearing housing 9.

[0051] An exhaust-side bearing housing 10 is provided on one side of the pressure-bearing housing 5, and a thrust bearing 11 is provided inside the exhaust-side bearing housing 10. The second end of the main shaft 2 is connected to the thrust bearing 11.

[0052] A shaft end seal 12 and a balance disc 13 are provided inside the pressure-bearing housing 5 and between it and the main shaft 2.

[0053] In this embodiment, an exhaust-side bearing housing 10 is provided on one side of the pressure-bearing housing 5. The exhaust-side bearing housing 10 and the lower pressure-bearing housing are integrally cast, improving connection performance and strength. A thrust bearing 11 is installed inside the exhaust-side bearing housing 10, and the second end of the main shaft 2 is stably connected to the thrust bearing 11. The thrust bearing 11 ensures that the main shaft 2 maintains a precise axial position during high-speed rotation, preventing the main shaft 2 from shifting due to axial force, which would affect the normal operation of the compressor. A shaft end seal 12 and a balance disc 13 are provided inside the pressure-bearing housing 5 and between the thrust bearing 11 and the main shaft 2. The shaft end seal 12 is mainly used to prevent gas leakage at the point where the main shaft 2 exits the pressure-bearing housing 5. It adopts a high-efficiency sealing structure, such as a dry gas seal or a floating ring seal, which is rationally selected based on factors such as the compressor's working pressure, temperature, and gas properties. The balance disc 13 is used to balance the axial force generated by the pressure difference on both sides of the impeller during compressor operation, further reducing the load on the thrust bearing 11.

[0054] In actual operation, gas enters the compressor through the inlet housing 4, and the main shaft 2 drives the impeller assembly to rotate at high speed. During rotation, the impellers perform work on the gas through their blades, increasing the gas's speed and pressure. After continuous compression by multiple impeller stages, the gas pressure gradually increases until it reaches the required pressure value and is discharged from the compressor from the exhaust side. The support bearing 7 and bearing seal 8 in the inlet-side bearing housing 6, and the thrust bearing 11 in the exhaust-side bearing housing 10, work together to ensure the stable operation of the main shaft 2. In addition, the shaft end seal 12 in the pressure housing 5 prevents gas leakage, and the balance disc 13 balances the axial force, jointly ensuring that the compressor can operate continuously in a highly efficient and stable state.

[0055] The impeller assembly includes a first impeller 14, a second impeller 15, a third impeller 16 and a fourth impeller 17 sequentially arranged on the main shaft 2, wherein the flow coefficient of the first impeller 14 is between 0.16 and 0.25.

[0056] A partition plate 18 is provided on the main shaft 2 and located between the first impeller 14, the second impeller 15, the third impeller 16 and the fourth impeller 17.

[0057] In this embodiment, the impeller assembly mainly consists of a first impeller 14, a second impeller 15, a third impeller 16, and a fourth impeller 17 sequentially arranged on the main shaft 2. A baffle 18 is also arranged on the main shaft 2 between these impellers. The flow coefficient of the first impeller 14 is controlled within the range of 0.16-0.25, enabling it to introduce gas at a suitable flow rate and perform initial compression. The second impeller 15 follows immediately after the first impeller 14, further pressurizing the gas based on the initial compression by the first impeller 14. The third impeller 16 and the fourth impeller 17 continue to bear the responsibility of progressively compressing the gas. As the gas passes through each impeller sequentially, its pressure and velocity continuously increase. The baffle 18, located between the first impeller 14, second impeller 15, third impeller 16, and fourth impeller 17 on the main shaft 2, is made of a special high-strength, low-friction alloy material. Its surface is finely polished and coated, possessing excellent smoothness and wear resistance. The baffle 18 separates each impeller into an independent compression chamber, effectively preventing gas from flowing between impellers and ensuring that each impeller can compress gas in an independent and stable environment, which greatly improves compression efficiency.

[0058] In actual operation, the gas first enters the first impeller 14. Under the centrifugal force generated by its high-speed rotation, the gas is initially compressed and accelerated. Then, it is guided into the second impeller 15 through the baffle 18 for secondary compression. This process continues until the gas is compressed in stages through the third impeller 16 and the fourth impeller 17, finally reaching the required pressure and flow rate, thus achieving efficient and stable compression of the gas.

[0059] An adjustable guide vane 19 is provided inside the air intake housing 4, and the adjustable guide vane 19 is located between the air intake side bearing housing 6 and the first impeller 14.

[0060] An actuator is provided outside the air intake housing 4 to drive the adjustable guide vane 19 to rotate. The actuator includes a bevel gear 20 and a gear ring 21. The bevel gear 20 is connected to the adjustable guide vane 19, and the gear ring 21 is meshed with the bevel gear 20.

[0061] In this embodiment, the adjustable guide vane 19 can flexibly adjust the angle and flow rate of gas entering the first impeller 14 according to the actual operating conditions of the compressor, thereby optimizing the compressor performance. The adjustable guide vane 19 consists of multiple blades connected together by a mechanical structure, enabling them to rotate synchronously. The blades are made of high-strength materials with good corrosion resistance to withstand the erosion of different gas media.

[0062] An actuator is installed outside the intake housing 4 to drive the adjustable guide vane 19 to rotate. This actuator mainly consists of a bevel gear 20 and a gear ring 21. The bevel gear 20 is connected to the rotating shaft of the adjustable guide vane 19, enabling the transmission of external driving force to the adjustable guide vane 19 for precise angle adjustment. The gear ring 21 meshes with the bevel gear 20; rotating the gear ring 21 drives the meshing bevel gear 20 to rotate, thereby adjusting the angle of the adjustable guide vane 19. Both the gear ring 21 and the bevel gear 20 are made of high-quality alloy steel and undergo a special heat treatment process to improve their hardness and wear resistance, ensuring stable and reliable power transmission during long-term high-speed operation and guaranteeing the precise adjustment of the adjustable guide vane 19.

[0063] The above are merely preferred embodiments of this application and are not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application. The above are merely preferred embodiments of this application. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of this application, and these improvements and modifications should also be considered within the protection scope of this application.

Claims

1. A large centrifugal compressor characterized by, The application relates to a shell assembly (1) provided with a gas passage along the axial direction of the shell assembly (1), a main shaft (2) arranged in the gas passage and provided with impeller groups arranged at intervals along the radial direction of the main shaft (2), and a heat preservation layer (3) arranged outside the shell. The shell assembly (1) comprises an air inlet shell (4) provided with an air inlet at the first end, a pressure bearing shell (5) connected with the second end of the air inlet shell (4) and provided with an air outlet at the second end, and the heat preservation layer (3) arranged outside the air inlet shell (4) and the pressure bearing shell (5). The air inlet shell (4) is provided with an air inlet side bearing box (6), the first end of the main shaft (2) is arranged in the air inlet side bearing box (6), and a support bearing (7) and a bearing sealing element (8) are arranged between the air inlet side bearing box (6) and the main shaft (2). A rib plate (9) is arranged between the air inlet side bearing box (6) and the air inlet shell (4).

2. The large centrifugal compressor of claim 1, wherein The pressure bearing shell (5) is provided with an air outlet side bearing box (10) on one side, the air outlet side bearing box (10) is provided with a thrust bearing (11), and the second end of the main shaft (2) is connected with the thrust bearing (11). The pressure bearing shell (5) is provided with an axial end sealing (12) and a balance disc (13) between the main shaft (2). The impeller groups comprise a first impeller (14), a second impeller (15), a third impeller (16) and a fourth impeller (17) arranged on the main shaft (2) in sequence, and the flow coefficient of the first impeller (14) is between 0.16 and 0.

25. A partition plate (18) is arranged on the main shaft (2) between the first impeller (14), the second impeller (15), the third impeller (16) and the fourth impeller (17).

3. The large centrifugal compressor of claim 2, wherein An adjustable guide vane (19) is arranged in the air inlet shell (4) and located between the air inlet side bearing box (6) and the first impeller (14).

4. The large centrifugal compressor of claim 3, wherein A driver is arranged outside the air inlet shell (4) and used for driving the adjustable guide vane (19) to rotate, the driver comprises a bevel gear (20) and a gear ring (21), the bevel gear (20) is connected with the adjustable guide vane (19), and the gear ring (21) is meshed and connected with the bevel gear (20).

5. The large centrifugal compressor of claim 4, wherein ​ 6. The large centrifugal compressor of claim 5, wherein ​ 7. The large centrifugal compressor according to claim 6, characterized in that ​ 8. The large centrifugal compressor of claim 7, wherein ​ 9. The large centrifugal compressor of claim 8, wherein, ​ 10. The large centrifugal compressor of claim 9, wherein, ​

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