CN118167667A - High-speed double-impeller centrifugal compressor - Google Patents

High-speed double-impeller centrifugal compressor Download PDF

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Publication number
CN118167667A
CN118167667A CN202410305180.8A CN202410305180A CN118167667A CN 118167667 A CN118167667 A CN 118167667A CN 202410305180 A CN202410305180 A CN 202410305180A CN 118167667 A CN118167667 A CN 118167667A
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CN
China
Prior art keywords
end cover
air
bearing
compressor
motor casing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202410305180.8A
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Chinese (zh)
Inventor
徐韬
唐云冰
殷文豪
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Changzhou E&e Turbo Power Co ltd
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Changzhou E&e Turbo Power Co ltd
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Filing date
Publication date
Application filed by Changzhou E&e Turbo Power Co ltd filed Critical Changzhou E&e Turbo Power Co ltd
Priority to CN202410305180.8A priority Critical patent/CN118167667A/en
Publication of CN118167667A publication Critical patent/CN118167667A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • F04D29/0516—Axial thrust balancing balancing pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/06—Lubrication
    • F04D29/063—Lubrication specially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/122—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/626—Mounting or removal of fans

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention discloses a high-speed double-impeller centrifugal compressor.A stator assembly is positioned in an inner cavity of a motor casing, and a rotor assembly passes through the stator assembly; the compressor comprises a first compressor, a second end cover, a gas transmission mechanism and a rotor assembly, wherein the first end cover is fixed with one end of a motor shell; the air compressor further comprises a second air compressor for counteracting axial force, the second end cover is fixed with the other end of the motor shell, the second air compressor comprises a second pressure shell and a second air compressing wheel, the second pressure shell is fixed with the second end cover, the other end of the rotor assembly penetrates through the second end cover and then is fixed with the second air compressing wheel, and the rotor assembly is in running fit with the second end cover; the motor casing is provided with an air exhaust channel communicated with the inner cavity, and the air transmission mechanism is connected with the air exhaust channel. The invention has the advantage of prolonging the service life.

Description

High-speed double-impeller centrifugal compressor
Technical Field
The invention relates to the technical field of centrifugal compressors, in particular to a high-speed double-impeller centrifugal compressor.
Background
Centrifugal air compressors were first developed at the end of the 19 th century, when they were mainly used for gas compression and power. At the beginning of the 20 th century, centrifugal air compressors began to be used for the production of industrial gases, such as oxygen, nitrogen, etc., with the continued development of mechanical manufacturing and air compression technologies. The design structure of the centrifugal air compressor is further improved in the 60 s of the 20 th century, so that the centrifugal air compressor can be better suitable for severe working environments such as high pressure, high temperature and high humidity. Since the 21 st century, centrifugal air compressors have been widely used with continued industrial development, and have achieved higher efficiency and performance. The centrifugal air compressor works on the principle that gas is compressed by centrifugal force and the compressed gas is discharged.
Compared with other types of air compressors, the centrifugal air compressor has the following technical characteristics:
High efficiency: because the centrifugal air compressor adopts the centrifugal compression principle, the compression efficiency is high, and higher air flow and higher pressure can be provided.
The stability is good: the centrifugal air compressor has higher stability, lower noise and lower vibration in the working process.
The maintenance is simple: the maintenance of the core type air compressor is simpler, and the core type air compressor is easy to maintain due to the simple structure and the lower failure rate.
The adaptability is wide: the centrifugal air compressor can adapt to higher working pressure and temperature, and is suitable for occasions with severe working environments.
Centrifugal air compressors have become one of the indispensable devices in modern industrial production. With the development of industry, the technology of centrifugal air compressors is continuously improved, and the application range of the centrifugal air compressors is also continuously expanded. At present, centrifugal air compressors have been widely used in various fields such as chemical industry, electronics, metallurgy, petroleum, pharmacy, construction, etc.
With the research of aerodynamics, the efficiency of the centrifugal compressor is continuously improved, and due to the successful development of technical keys such as high-pressure sealing, processing of a small-flow narrow impeller, a multi-oil wedge bearing and the like, a series of problems that the centrifugal compressor develops to a high-pressure and wide-flow range are solved, so that the application range of the centrifugal compressor is greatly expanded, and the centrifugal compressor can replace a reciprocating compressor in many occasions, and the application range is greatly expanded.
In the important fields of electronics, nuclear power, aerospace and the like, the requirements on the oil content, dust content and pressure dew point of compressed gas are very high, and the centrifugal compressor is required to provide stable, continuous and clean compressed air so as to ensure the operation stability of associated equipment. The centrifugal air compressor is used as a power element of a pneumatic system, and becomes one of key equipment in the important field by virtue of the characteristics of small mass, large pressure, small vibration and the like.
Centrifugal compressors generally consist of a high-speed motor and a compressor connected with the high-speed motor, the rotating speed of the high-speed motor is generally between 6 and 12 ten thousand per minute according to the required compression ratio, such high rotating speed leads to very large heating value of the high-speed motor, in the prior art, a cooling structure is generally arranged on a motor shell, and the cooling structure can only act on a stator of the motor in a heat transfer mode and cannot act on a rotor.
On the other hand, when a centrifugal compressor is used for industrial gas suction, although a sealing structure is provided between the compressor and the high-speed motor, a small portion of the compressed gas generated at the compressor side flows into the high-speed motor due to the pressure effect generated by the compressor, and the adverse effect caused by this condition is as follows: (1) Since industrial gases are often accompanied by some special properties such as common corrosiveness or hardening of grease for lubricating bearings by chemical reaction, parts such as bearings, rotors, etc. of high-speed motors are easily damaged after long-term use. (2) The air pressure causes the air compressing wheel to receive axial acting force, so that the air compressing wheel is stressed in an unbalanced way in the axial direction, and the abrasion of parts such as the air compressing wheel, the end cover and the like is increased to cause the damage.
Disclosure of Invention
The invention provides a high-speed double-impeller centrifugal compressor capable of prolonging service life.
The high-speed double-impeller centrifugal compressor comprises a high-speed motor, a compressor and a first end cover, wherein the high-speed motor comprises a motor shell, a stator assembly and a rotor assembly, the motor shell is provided with an inner cavity, the stator assembly is positioned in the inner cavity of the motor shell, and the rotor assembly penetrates through the stator assembly; the air compressor comprises a first air compressor, wherein the first end cover is fixed with one end of the motor shell, the first air compressor comprises a first pressure shell and a first air compressing wheel, the first pressure shell is fixed with the first end cover, one end of the rotor component penetrates through the first end cover and then is fixed with the first air compressing wheel, and the rotor component is in rotary fit with the first end cover and further comprises a second end cover and an air conveying mechanism;
The air compressor further comprises a second air compressor for counteracting axial force, the second end cover is fixed with the other end of the motor shell, the second air compressor comprises a second pressure shell and a second air compressing wheel, the second pressure shell is fixed with the second end cover, the other end of the rotor assembly penetrates through the second end cover and then is fixed with the second air compressing wheel, and the rotor assembly is in running fit with the second end cover;
The motor casing is provided with an air exhaust channel communicated with the inner cavity, and the air transmission mechanism is connected with the air exhaust channel.
The beneficial effects of the invention are as follows:
1. The design of the double compressors is adopted, so that the axial force is effectively counteracted, the reliability of the compressors is improved, and the service life of the compressors is prolonged.
2. The permanent magnet high-speed direct current motor is adopted, so that the rotating speed and the efficiency of the compressor are greatly improved.
3. And the grease lubricated angular contact bearing is adopted, so that a complex lubricating oil system is simplified.
4. The tightness of the motor is improved by adopting a comb tooth technology, a sealing ring technology and a balanced differential pressure system.
5. The compressors connected in series at the two ends of the rotor assembly improve the pressure ratio and the gas compression.
Drawings
Fig. 1 is a sectional view of a high-speed twin-impeller centrifugal compressor of the present invention.
Fig. 2 is a schematic view of a part of the component shown in fig. 1 hidden.
Fig. 3 is a perspective view of a motor housing.
Fig. 4 is a cross-sectional view of a motor housing.
Fig. 5 is a perspective view of the first end cap.
Fig. 6 is a perspective view of the second end cap.
The reference symbols in the drawings:
The motor comprises a motor 1, a motor casing 10, an inner cavity 10a, an input port 10b, an output port 10c, a stator assembly 11, a stator 11a, a heat conducting sleeve 11b, a runner 11c, a rotor assembly 12, a first shaft shoulder 12a, a second shaft shoulder 12b, a wire 13 and a spring 14.
The device comprises a compressor 2, a first press shell 20, a first press wheel 21, a second press shell 22, a second press wheel 23, a first airflow director 24 and a second airflow director 25.
A first end cap 3, a first comb ring 3a, a first annular mounting portion 3b, a first bearing chamber 3c, a first bearing 3d, a first shaft seal 3e.
A second end cap 4, a second comb ring 4a, a second annular mounting portion 4b, a second bearing chamber 4c, a second bearing 4d, and a second bearing 4e.
A gas transmission mechanism 5 and a pressure sensor 6.
The device comprises a first drainage notch a, an axial hole b, a radial hole c, a first drainage channel d, an air passage e, a first abdication channel f, a second drainage notch g and a second drainage channel h.
Detailed Description
As shown in fig. 1 to 6, a high-speed double-impeller centrifugal compressor of the present invention includes a high-speed motor 1, a compressor 2, a first end cover 3, a second end cover 4, and a gas delivery mechanism 5, which will be described in detail below.
The high-speed motor 1 in this embodiment adopts a permanent magnet motor, the high-speed motor 1 includes a motor casing 10, a stator assembly 11, and a rotor assembly 12, the motor casing 10 has an inner cavity 10a, the inner cavity 10a is a through hole axially opened along the motor casing 10, the stator assembly 11 is located in the inner cavity 10a of the motor casing 10, and the rotor assembly 12 passes through the stator assembly 11.
The compressor 2 includes a first compressor, the first end cover 3 is fixed to one end of the motor casing 10, for example, the first end cover 3 is preferably fixed to one end of the motor casing 10 by a screw, a first annular groove is disposed on an axial end surface of the motor casing 10 facing the first end cover 3, a first sealing ring is installed in the first annular groove, and the first end cover 3 and the motor casing 10 form a seal through the first sealing ring.
The first compressor comprises a first pressure shell 20 and a first pressure wheel 21, the first pressure shell 20 is fixed with the first end cover 3, the other ends of the first pressure shell 20 and the first end cover 3 are preferably fixed by screws, a plurality of concentric first comb tooth rings 3a are arranged on the axial end face of the first end cover 3 facing the first pressure wheel 21, the first pressure wheel 21 and the first comb tooth rings 3a are matched to form comb tooth seals, and because the number of the first comb tooth rings 3a is multiple, air flow is blocked when passing through each first comb tooth ring 3a, so that the sealing purpose is achieved.
The first compressor further comprises a first airflow director 24, a first annular mounting portion 3b is arranged on the axial end surface of the first end cover 3 facing the first compressor wheel 21, a plurality of first comb tooth rings 3a are located in the area surrounded by the first annular mounting portion 3b, the first airflow director 24 is sleeved on the first annular mounting portion 3b, the first airflow director 24 is clamped between the first pressure shell 20 and the first end cover 3 in the axial direction, and the first airflow director 24 is clamped between the first pressure shell 20 and the first end cover 3 in the radial direction. Since the first airflow director 24 is provided with a plurality of channels, but the total volume of the channels is smaller than the volume of the diffusion channels in the first pressure shell 20, when the first compressor wheel 21 compresses the air, the compressed air is required to flow through the first airflow director 24, and the pressure of the compressed air is further improved by the action of the first airflow director 24.
One end of the rotor assembly 12 passes through the first end cover 3 and then is fixed with the first air compressing wheel 21, and the rotor assembly 12 is in rotating fit with the first end cover 3. The first end cover 3 is provided with a first bearing chamber 3c, a first bearing 3d and a first shaft seal 3e are arranged in the first bearing chamber 3c, the first bearing 3d is preferably an angular contact bearing lubricated by grease, the rotor assembly 12 is provided with a first shaft shoulder 12a, one end of the rotor assembly 12 passes through the first bearing 3d, then one end of the first bearing 3d abuts against the first shaft shoulder 12a, the other end of the first bearing 3d abuts against one end of the first shaft seal 3e, and the other end of the first shaft seal 3e abuts against the first air compressing wheel 21. The first shaft seal 3e is provided with a first ring groove on the peripheral surface, and a first sealing ring is installed in the first ring groove, and the sealing purpose is achieved by matching the first sealing ring with the inner wall surface of the first bearing chamber 3 c.
Therefore, for the first air compressor, the sealing performance is improved by adopting the comb tooth technology and the sealing ring technology, and the air leakage quantity of the lateral high-speed motor 1 of the first air compressor is reduced.
The compressor 2 further includes a second compressor, the second end cover 4 is fixed to the other end of the motor casing 10, for example, the second end cover 4 is preferably fixed to the other end of the motor casing 10 by using a screw, a second annular groove is disposed on an axial end surface of the motor casing 10 facing the second end cover 3, a second sealing ring is installed in the second annular groove, and the second end cover 4 and the motor casing 10 form a seal through the second sealing ring.
The second compressor comprises a second pressure shell 22 and a second pressure wheel 23, the second pressure shell 22 is fixed with the second end cover 4, and the other ends of the second pressure shell 22 and the second end cover 4 are preferably fixed by screws. In this embodiment, the output end of the first pressure shell 20 is connected to the input end of the second pressure shell 22, that is, the compressed gas output from the first compressor is further provided to the second compressor, and is further compressed by the second compressor. In addition, in the present invention, by installing the first compressor at one end of the rotor assembly 12 and installing the second compressor at the other end of the rotor assembly 12, based on such a structure, even if there are cases where the first compressor and the second compressor generate axial force respectively, since the directions of the two axial force are opposite, such a structure effectively counteracts the axial force, avoids friction and abrasion between parts, and thus improves the reliability and lifetime of the compressor.
The axial end face of the second end cover 4, which faces the second air compressing wheel 23, is provided with a plurality of concentric second comb tooth rings 4a, and the second air compressing wheel 23 and the second comb tooth rings 4a are matched to form comb tooth sealing, and as the number of the second comb tooth rings 4a is multiple, air flow is blocked when passing through each second comb tooth ring 4a, and the sealing purpose is achieved.
The second compressor further comprises a second airflow director 25, a second annular mounting portion 4b is arranged on the axial end face of the second end cover 4 facing the second compressor wheel 23, a plurality of second comb teeth rings 4a are located in the area surrounded by the second annular mounting portion 4b, the second airflow director 25 is sleeved on the second annular mounting portion 4b, and the second annular mounting portion 4b is clamped between the second pressure shell 22 and the second end cover 4 in the axial direction. In the radial direction, the second air flow guide 25 is clamped between the second press shell 22 and the second end cap 4. Since the second airflow director 25 is provided with a plurality of channels, but the total volume of the channels is smaller than the volume of the diffusion channels in the second pressure shell 22, when the second compressor wheel 23 compresses the air, the compressed air will flow through the second airflow director 25, and the pressure of the compressed air is further improved by the action of the second airflow director 25.
The high-speed motor 1 in the embodiment further comprises a spring 14, the other end of the rotor assembly 12 passes through the second end cover 4 and then is fixed with the second air compressing wheel 23, and the rotor assembly 12 is in running fit with the second end cover 4. The second end cover 4 is provided with a second bearing chamber 4c, a second bearing 4d and a second bearing 4e are arranged in the second bearing chamber 4c, the second bearing 4d is preferably an angular contact bearing lubricated by grease, the spring 14 is positioned in the second bearing chamber 4c and sleeved on the rotor assembly 12, the rotor assembly 12 is provided with a second bearing shoulder 12b, after the other end of the rotor assembly 12 passes through the second bearing 4d and the spring 14, one end of the spring 14 is matched with the bottom wall of the second bearing chamber 4c, one end of the second bearing 4d is matched with the other end of the spring 14 and the second bearing shoulder 12b, the other end of the second bearing 4d is propped against one end of the second bearing 4e, and the other end of the second bearing 4e is propped against the second air compressing wheel 23.
The second seal 4e has a second annular groove on its peripheral surface, in which a second seal ring is installed, and the second seal ring is engaged with the inner wall surface of the second bearing chamber 4c to achieve the sealing purpose. In addition, through the action of the spring 14, when the axial acting force generated by the first air compressor and the second air compressor is unequal, and the axial acting force is transmitted to the spring 14, a part of acting force can be counteracted through compression of the spring 14, so that the axial displacement of the rotor assembly is reduced, the contact between the air compressing wheel and the comb ring on the end cover is avoided, or the contact amount between the air compressing wheel and the comb ring is reduced, and abrasion is further reduced.
The motor casing 10 is provided with an air suction channel communicated with the inner cavity 10a, and the air conveying mechanism 5 is connected with the air suction channel. The air exhaust channel comprises a first drainage notch a, an axial hole b and a radial hole c, wherein the first drainage notch a is arranged on the axial end face of one end of the motor casing 10 and is communicated with the inner cavity 10a, and after the first end cover 3 is tightly attached to one end of the motor casing 10, a first drainage channel d is formed between the first end cover 3 and the motor casing 10 through the first drainage notch a. The orifice of one end of the axial hole b is communicated with the first drainage channel d, the radial hole c is positioned on the peripheral surface of the motor casing 10 and is communicated with the axial hole b, and the gas transmission mechanism 5 is matched with the axial hole b. The gas delivery mechanism 5 comprises a suction nozzle, a gas delivery machine, one end of the suction nozzle being fitted with a radial hole c, the other end of the suction nozzle being connected to the gas delivery machine.
The air exhaust channel further comprises a second drainage notch g, the second drainage notch g is arranged on the axial end face of the other end of the motor casing 10 and is communicated with the inner cavity 10a, after the second end cover 4 is tightly attached to the other end of the motor casing 10, a second drainage channel h is formed between the second end cover 4 and the motor casing 10 through the second drainage notch g, and an orifice at the other end of the axial hole b is communicated with the second drainage channel h.
In this embodiment, when the first compressor and the second compressor work, a part of the generated compressed gas will be strung into the inner cavity 10a, if the gas damaging the high-speed motor is input to the first compressor, the gas strung into the inner cavity 10a is rapidly taken away by the negative pressure acting force generated by the gas transmission mechanism 5, so as to reduce the damage to the high-speed motor to the maximum extent. On the other hand, the negative pressure acting force generated by the gas transmission mechanism 5 enables gas to flow rapidly, and performs heat exchange with the high-speed motor 1, so that a heat dissipation effect is formed on the high-speed motor 1, the magnetic property of the magnetic steel is prevented from being reduced, and the performance of the high-speed motor is ensured.
The high-speed motor 1 further comprises a lead wire 13, the air extraction channel further comprises an air passage e used for being communicated with the atmosphere, the air passage e is positioned on the peripheral surface of the motor casing 10 and is communicated with the inner cavity 10a, one end of the lead wire 13 is connected with the stator assembly 11, and the other end of the lead wire 13 passes through the air passage e and is exposed to the outside of the motor casing 10. The air passage e not only allows the lead 13 to pass through, but also allows the inner cavity 10 to communicate with the atmosphere, even if compressed air on the compressor side does not flow into the inner cavity 10a, the flowing atmosphere can take away heat generated by the high-speed motor when the air conveying mechanism 5 works due to the fact that the atmosphere enters the inner cavity 10a, and therefore the heat dissipation effect is achieved.
The length of the stator assembly 11 is smaller than that of the motor casing 10, and a first yielding channel f through which air flows is formed between the stator assembly 11 and the first end cover 3 and is communicated with the first drainage channel d. The stator assembly 11 comprises a stator 11a and a heat conducting sleeve 11b, wherein the stator 11a is positioned in the heat conducting sleeve 11b and is combined and fixed with the heat conducting sleeve 11b in a concave-convex structure, a flow channel 11c for cooling medium is arranged on the outer peripheral surface of the heat conducting sleeve 11b, the heat conducting sleeve 11b is positioned in the motor casing 10 and is fixed with the motor casing 10, a cooling channel which is sealed between the heat conducting sleeve 11b and the motor casing 10 and is used for cooling medium to flow through is formed, and an input port 10b and an output port 10c which are communicated with the cooling channel are arranged on the motor casing 10.
The working process of the high-speed double-impeller centrifugal compressor is as follows: when the gas flows through the first air compressing wheel 21 of the centrifugal compressor, the first air compressing wheel 21 rotating at high speed makes the gas have a pressure increased under the action of centrifugal force, and the speed is greatly increased, and the compressed gas can be further pressurized because the outlet of the first air compressor is connected with the inlet of the second air compressor. In the compression process, the arranged comb tooth sealing structure can play a role in sealing and blocking, the first shaft seal 3e and the second shaft seal 4e are further sealed, compressed gas is reduced from being strung into the inner cavity 10a, and the sealing effect is achieved.
A small amount of compressed gas still enters the inner cavity 10a of the motor casing 10 in the whole compression process, if the gas transmission mechanism 5 is not started, the compressed gas is discharged to the atmosphere along the air passage e, and if the gas transmission mechanism 5 is started, the compressed gas is pumped away by the gas transmission mechanism 5.
In addition, the invention further comprises a pressure sensor 6 and a controller (not shown in the figure), wherein the pressure sensor 6 is arranged on the motor casing 10, the first pressure casing 20 and the second pressure casing 22, the pressure sensor 6 positioned on the motor pressure 10 is communicated with the air suction channel or the inner cavity 10a, the pressure sensor 6 and the air transmission mechanism 5 are electrically connected with the controller, and the controller is preferentially in PLC, so that according to the pressure values in the first pressure casing 20, the second pressure casing 22 and the inner cavity 10a, the air transmission mechanism 5 is controlled by the controller to automatically suck air or balance the pressure difference at two sides of the inner cavity 10a, thereby avoiding adverse effects caused by air leakage.

Claims (10)

1. The high-speed double-impeller centrifugal compressor comprises a high-speed motor (1), a compressor (2) and a first end cover (3), wherein the high-speed motor (1) comprises a motor shell (10), a stator assembly (11) and a rotor assembly (12), the motor shell (10) is provided with an inner cavity (10 a), the stator assembly (11) is positioned in the inner cavity (10 a) of the motor shell (10), and the rotor assembly (12) penetrates through the stator assembly (11); the compressor (2) comprises a first compressor, the first end cover (3) is fixed with one end of the motor casing (10), the first compressor comprises a first pressure casing (20) and a first air compressing wheel (21), the first pressure casing (20) is fixed with the first end cover (3), one end of the rotor component (12) penetrates through the first end cover (3) and then is fixed with the first air compressing wheel (21), and the rotor component (12) is in running fit with the first end cover (3), and the compressor is characterized by further comprising a second end cover (4) and an air conveying mechanism (5);
The compressor (2) further comprises a second compressor for counteracting axial force, the second end cover (4) is fixed with the other end of the motor casing (10), the second compressor comprises a second pressure casing (22) and a second air compressing wheel (23), the second pressure casing (22) is fixed with the second end cover (4), the other end of the rotor assembly (12) passes through the second end cover (4) and then is fixed with the second air compressing wheel (23), and the rotor assembly (12) is in running fit with the second end cover (4);
the motor casing (10) is provided with an air exhaust channel communicated with the inner cavity (10 a), and the air transmission mechanism (5) is connected with the air exhaust channel.
2. The high-speed double-impeller centrifugal compressor according to claim 1, wherein the air extraction channel comprises a first drainage notch (a), an axial hole (b) and a radial hole (c), the first drainage notch (a) is arranged on the axial end face of one end of the motor casing (10) and is communicated with the inner cavity (10 a), and after the first end cover (3) is tightly attached to one end of the motor casing (10), a first drainage channel (d) is formed between the first end cover (3) and the motor casing (10) through the first drainage notch (a);
The orifice at one end of the axial hole (b) is communicated with the first drainage channel (d), the radial hole (c) is positioned on the peripheral surface of the motor casing (10) and is communicated with the axial hole (b), and the gas transmission mechanism (5) is matched with the axial hole (b).
3. The high-speed double-impeller centrifugal compressor according to claim 2, wherein the air extraction channel further comprises a second drainage notch (g), the second drainage notch (g) is arranged on the axial end face of the other end of the motor casing (10) and is communicated with the inner cavity (10 a), and after the second end cover (4) is tightly attached to the other end of the motor casing (10), a second drainage channel (h) is formed between the second end cover (4) and the motor casing (10) through the second drainage notch (g);
the orifice at the other end of the axial hole (b) is communicated with the second drainage channel (h).
4. A high-speed twin-impeller centrifugal compressor according to claim 2, wherein the high-speed motor (1) further comprises a wire (13), the suction passage further comprises an air passage (e) for communicating with the atmosphere, the air passage (e) being located on the peripheral surface of the motor casing (10) and communicating with the inner cavity (10 a); one end of the wire (13) is connected with the stator assembly (11), and the other end of the wire (13) passes through the air passage (e) to be exposed outside the motor casing (10).
5. A high-speed double-impeller centrifugal compressor according to any one of claims 2-4, wherein the stator assembly (11) has a length smaller than the length of the motor casing (10), and a first relief channel (f) is formed between the stator assembly (11) and the first end cap (3) through which the air flow passes, the first relief channel (f) being in communication with the first drainage channel (d).
6. The high-speed double-impeller centrifugal compressor according to claim 5, wherein the stator assembly (11) comprises a stator (11 a) and a heat conducting sleeve (11 b), the stator (11 a) is positioned in the heat conducting sleeve (11 b) and combined and fixed with the heat conducting sleeve (11 b) in a concave-convex structure, a runner (11 c) for cooling medium is arranged on the outer peripheral surface of the heat conducting sleeve (11 b), the heat conducting sleeve (11 b) is positioned in the motor casing (10) and fixed with the motor casing (10), a sealed cooling channel for cooling medium to flow is formed between the heat conducting sleeve (11 b) and the motor casing (10), and an input port (10 b) and an output port (10 c) which are communicated with the cooling channel are arranged on the motor casing (10).
7. The high-speed double-impeller centrifugal compressor according to claim 1, wherein a plurality of concentric first comb tooth rings (3 a) are arranged on the axial end surface of the first end cover (3) facing the first air compressing wheel (21), and the first air compressing wheel (21) and the first comb tooth rings (3 a) form comb tooth seals after being matched;
the axial end face of the second end cover (4) facing the second air compressing wheel (23) is provided with a plurality of concentric second comb tooth rings (4 a), and the second air compressing wheel (23) and the second comb tooth rings (4 a) are matched to form comb tooth sealing.
8. The high-speed double-impeller centrifugal compressor according to claim 7, wherein the first compressor further comprises a first airflow director (24), a first annular mounting portion (3 b) is arranged on the axial end face of the first end cover (3) facing the first air compressing wheel (21), a plurality of first comb teeth rings (3 a) are located in the area surrounded by the first annular mounting portion (3 b), the first airflow director (24) is sleeved on the first annular mounting portion (3 b), and the first airflow director (24) is clamped between the first pressure shell (20) and the first end cover (3).
9. A high speed twin vane centrifugal compressor according to claim 7, wherein the second compressor further comprises a second air flow guide (25), the axial end surface of the second end cover (4) facing the second compressor wheel (23) is provided with a second annular mounting portion (4 b), a plurality of second comb teeth rings (4 a) are located in the area surrounded by the second annular mounting portion (4 b), the second air flow guide (25) is sleeved on the second annular mounting portion (4 b), and the second air flow guide (25) is clamped between the second casing (22) and the second end cover (4).
10. The high-speed double-impeller centrifugal compressor according to claim 1, wherein the high-speed motor (1) further comprises a spring (14), a first bearing chamber (3 c) is arranged on the first end cover (3), a first bearing (3 d) and a first shaft seal (3 e) are arranged in the first bearing chamber (3 c), a first shaft shoulder (12 a) is arranged on the rotor assembly (12), one end of the rotor assembly (12) passes through the first bearing (3 d), after passing through the first bearing (3 d), one end of the first bearing (3 d) abuts against the first shaft shoulder (12 a), the other end of the first bearing (3 d) abuts against one end of the first shaft seal (3 e), and the other end of the first shaft seal (3 e) abuts against the first air compressing wheel (21);
the second end cover (4) is provided with a second bearing chamber (4 c), a second bearing (4 d) and a second bearing (4 e) are arranged in the second bearing chamber (4 c), the spring (14) is arranged in the second bearing chamber (4 c) and sleeved on the rotor assembly (12), the rotor assembly (12) is provided with a second bearing shoulder (12 b), one end of the spring (14) is matched with the bottom wall of the second bearing chamber (4 c) after the other end of the rotor assembly (12) passes through the second bearing (4 d) and the spring (14), one end of the second bearing (4 d) is matched with the other end of the spring (14) and the second bearing shoulder (12 b), the other end of the second bearing (4 d) is propped against one end of the second bearing (4 e), and the other end of the second bearing (4 e) is propped against the second air compressing wheel (23).
CN202410305180.8A 2024-03-18 2024-03-18 High-speed double-impeller centrifugal compressor Pending CN118167667A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202410305180.8A CN118167667A (en) 2024-03-18 2024-03-18 High-speed double-impeller centrifugal compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202410305180.8A CN118167667A (en) 2024-03-18 2024-03-18 High-speed double-impeller centrifugal compressor

Publications (1)

Publication Number Publication Date
CN118167667A true CN118167667A (en) 2024-06-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202410305180.8A Pending CN118167667A (en) 2024-03-18 2024-03-18 High-speed double-impeller centrifugal compressor

Country Status (1)

Country Link
CN (1) CN118167667A (en)

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