CN212225523U - Variable-frequency medium-pressure double-screw air compressor - Google Patents

Abstract

The utility model provides a variable-frequency medium-pressure twin-screw air compressor, comprising: a double-shaft motor, the double-shaft motor is a variable-frequency motor; a first-stage body and a second-stage body, the double-shaft motor and the first-stage body The body and the second-stage body are respectively connected and driven in both directions; a first-stage cooling system is arranged between the first-stage body and the second-stage body to cool the compressed gas and lubricating oil flowing from the first-stage body to the second-stage body ; The water removal system is arranged between the first-stage body and the second-stage body, and is used for drying the compressed gas and lubricating oil flowing from the first-stage body to the second-stage body. The variable frequency medium-pressure twin-screw air compressor of the utility model can compress the air to 2.5-4.0MPa, which meets the needs of different medium-pressure industries, and has the advantages of low cost, simple maintenance and stable performance.

Description

Inverter medium pressure twin screw air compressor

technical field

The utility model relates to a frequency conversion type medium-pressure twin-screw air compressor.

Background technique

Air compressor is a device that increases gas pressure by compressing air, and is widely used in metallurgy, machinery manufacturing, petrochemical, electronic equipment, medical, textile, food and other industries. At present, most twin-screw compressors on the market can provide pressures generally lower than 2.5Mpa.

With the increasing number of domestic industries that require air pressure at 2.5-4.0MPa, the market demand for medium-pressure units is increasing. However, due to the limitation of high internal pressure ratio, conventional single-stage screw compressors are rarely used in Medium-pressure units; piston compression and single-screw two-stage compressors have high costs, unstable performance, and easy wear of the star wheel.

Utility model content

The technical problem to be solved by the utility model is to overcome the limitation of the conventional common single-stage screw compressor in the prior art, which is rarely used in medium-pressure units due to the high internal pressure ratio; piston compression and single-screw two-stage compressors have high costs. , the performance is unstable, and the star wheel is easy to wear and tear, and a variable frequency medium pressure twin-screw air compressor is provided.

The utility model solves the above-mentioned technical problems through the following technical solutions:

A variable-frequency medium-pressure twin-screw air compressor is characterized in that the variable-frequency medium-pressure twin-screw air compressor comprises:

a double output shaft motor, the double output shaft motor is a variable frequency motor;

A first-stage body and a second-stage body, and the double-shaft motor is connected to the first-stage body and the second-stage body respectively and transmits bidirectionally;

a first-stage cooling system, arranged between the first-stage body and the second-stage body, for cooling the compressed gas and lubricating oil flowing from the first-stage body to the second-stage body;

The water removal system is arranged between the first-stage body and the second-stage body, and is used for drying the compressed gas and lubricating oil flowing from the first-stage body to the second-stage body.

In the utility model, the coaxial bidirectional coupling of a double-outlet motor is used for transmission, so the transmission loss is small and the efficiency is high. The dual-shaft motor is controlled by frequency conversion, which effectively reduces the impact on the power grid during startup and improves the energy-saving efficiency of the compressor. It can meet the multi-stage different pressure requirements, and the pressure range can be from 2.5-4.0Mpa.

Among them, a first-stage cooling system is used to cool a first-stage compressed gas and lubricating oil, and the second-stage approximate isothermal compression is realized to improve the volumetric efficiency, ensure that the compressor oil is used in normal temperature conditions, and prolong its service life. The water removal system is used to ensure the drying of the compressed gas in the second stage, and prevent the rotor and bearings of the second stage body from rusting, wearing and getting stuck due to the inhalation of condensed water.

Preferably, the second-stage body adopts a mechanical shaft seal and is filled with lubricating oil, which can ensure the impact of the second-stage body on the shaft seal when the intake pressure is high, prevent the shaft seal from being damaged, and ensure that the shaft seal leaks when the body is running.

Preferably, the one-stage cooling system is a one-stage air cooler.

Preferably, the water removal system sequentially includes a mechanical water separator and a precision water separator.

Preferably, the water removal system sequentially includes a mechanical water separator, a freeze dryer and a precision gas-water separator.

Preferably, a section of the body is connected to a section of oil and gas separation cylinder, a section of oil and gas separation core, a section of pressure maintenance valve and the section of cooling system in sequence.

Preferably, the second-stage body is sequentially connected to the second-stage oil and gas separation cylinder, the second-stage oil and gas separation core, the second-stage pressure maintenance valve and the second-stage gas cooler. When the machine is shut down, the discharge of the second-stage body is discharged to the first-stage oil and gas separator through the mechanical discharge proportional valve and the pressure reducing valve to reduce the discharge noise and ensure the discharge safety.

Preferably, an oil-water detector is installed at the bottom of the second-stage oil and gas separation cylinder. When the water content in the lubricating oil exceeds the set value of the PLC, the PLC will alarm and prompt, and the machine will stop to drain to prevent the lubricating oil from emulsification.

Preferably, the first-stage oil and gas separation core supplies air to the second-stage body through a gas supplement solenoid valve and a one-way valve.

Preferably, a check valve is installed on both the intake end and the exhaust end of the two-stage body. The check valves on both sides prevent air pressure recoil during operation, shutdown, and emergency stop, which will cause damage to the first-stage compression system; at the same time, prevent the backflow of lubricating oil from the second-stage body causing difficulty in secondary starting.

Preferably, the dual-shaft motor is controlled by a PLC frequency conversion. Further use multiple pressure and temperature sensors to detect the relevant signals of each section, and feedback the signals to the PLC to achieve multi-level protection function and improve the safety performance of the compressor.

Preferably, a pre-filtered muffler box is installed before a section of the air filter. The pre-filtered muffler box is composed of a filter screen, a flame-retardant muffler cotton and a sheet metal cover, which can filter larger particles in the air and reduce the amount of noise generated during discharge. noise.

The positive improvement effect of the utility model is that the variable frequency medium pressure twin-screw air compressor of the utility model can compress the air to 2.5-4.0MPa, which can meet the needs of different medium pressure industries, and has low cost, simple maintenance and stable performance.

Description of drawings

FIG. 1 is a schematic diagram of a mechanical structure of a variable frequency medium-pressure twin-screw air compressor according to a preferred embodiment of the present invention.

FIG. 2 is another schematic diagram of the mechanical structure of the variable-frequency medium-pressure twin-screw air compressor according to the preferred embodiment of the present invention.

3 is a schematic diagram of the overall pipeline connection of the variable frequency medium-pressure twin-screw air compressor according to the preferred embodiment of the present invention.

4 is a schematic diagram of a partial pipeline connection of the variable frequency medium pressure twin-screw air compressor according to the preferred embodiment of the present invention.

Detailed ways

A preferred embodiment is given below, and the present utility model will be more clearly and completely described with reference to the accompanying drawings.

As shown in Figures 1-4, the medium-pressure twin-screw air compressor of this embodiment includes a section of oil and gas separation cylinder 1, a section of oil and gas separation core 2, an oil cooler 3, a temperature control valve 4, an oil filter 5, and an oil return. One-way valve 6, integrated intake valve 7, first-stage air filter 8, first-stage air cooler 9, first-stage pressure maintenance valve 10, check valve 11, pressure reducing valve 12, check valve 13, dual-shaft motor 14 , one-stage body 15, check valve 16, normally closed solenoid valve 17, relief valve 18, oil return check valve 19, second-stage body 20, check valve 21, mechanical shaft seal 22, oil filter 23, oil cooling 24, temperature control valve 25, two-stage oil and gas separation cylinder 26, two-stage oil and gas separation core 27, two-stage pressure maintenance valve 28, two-stage air cooler 29, mechanical water separator 30, precision water separator 31, Automatic drain valve 32, PLC33, freeze desiccant 34, air supply solenoid valve 35, oil and water detector 36, pre-filter muffler box 37.

As shown in FIGS. 1-4 , this embodiment includes a variable-frequency medium-pressure twin-screw air compressor. The variable-frequency medium-pressure twin-screw air compressor includes a double-shaft motor 14 , which is a variable-frequency motor. The variable frequency medium pressure twin-screw air compressor also includes a first-stage body 15 and a second-stage body 20, and the double-shaft motor 14 is connected to the first-stage body 15 and the second-stage body 20 respectively and is bidirectionally driven.

As shown in Figures 1-4, the variable frequency medium pressure twin-screw air compressor of this embodiment includes a first-stage cooling system, which is arranged between the first-stage body 15 and the second-stage body 20, and is used to cool the flow from the first-stage body 15 to the second-stage body. Compressed gas and lubricating oil of the body 20;

As shown in Figures 1-4, the variable frequency medium pressure twin-screw air compressor of this embodiment includes a water removal system, which is arranged between the first-stage body 15 and the second-stage body 20, and is used for drying to flow from the first-stage body 15 to the second-stage body. Compressed gas and lubricating oil of the body 20 .

In the utility model, a double-outlet motor 14 is used for transmission with a coaxial bidirectional coupling, which has small transmission loss and high efficiency. The double output shaft motor 14 is controlled by frequency conversion, which effectively reduces the impact on the power grid during startup and improves the energy-saving efficiency of the compressor. It can meet the multi-stage different pressure requirements, and the pressure range can be from 2.5-4.0Mpa.

Among them, a first-stage cooling system is used to cool a first-stage compressed gas and lubricating oil, and the second-stage approximate isothermal compression is realized to improve the volumetric efficiency, ensure that the compressor oil is used in normal temperature conditions, and prolong its service life. The water removal system is used to ensure the drying of the compressed gas in the second stage, and prevent the rotor and bearings of the second stage body 20 from rusting, wearing and getting stuck due to the inhalation of condensed water.

As shown in FIG. 3 , the second-stage body 20 of this embodiment adopts a mechanical shaft seal and is filled with lubricating oil, which can ensure the impact of the second-stage body 20 on the shaft seal when the intake pressure is high, prevent damage to the shaft seal, and ensure The shaft seal leaks when the body is running.

As shown in FIG. 3 , the first-stage cooling system in this embodiment is a first-stage air cooler 9 . The water removal system sequentially includes a mechanical water separator 30 and a precision water separator 31 . Alternatively, as shown in FIG. 4 , the water removal system includes a mechanical water separator 30 , a freeze dryer 34 and a precision gas-water separator 31 in sequence.

As shown in FIG. 3 , a section of the body 15 in this embodiment is sequentially connected to a section of oil and gas separation cylinder 1 , a section of oil and gas separation core 2 , a section of pressure maintenance valve 10 and a section of cooling system.

As shown in FIG. 3 , the second-stage body 20 of this embodiment is sequentially connected to the second-stage oil and gas separation cylinder 26 , the second-stage oil and gas separation core 27 , the second-stage pressure maintenance valve 28 and the second-stage air cooler 29 . During shutdown, the discharge of the second-stage body 20 is discharged into the first-stage oil and gas separation cylinder 1 through the mechanical discharge proportional valve and the pressure reducing valve, so as to reduce the discharge noise and ensure the discharge safety.

As shown in FIG. 3 , an oil-water detector 36 is installed at the bottom of the second-stage oil-gas separation cylinder of this embodiment. When the water content in the lubricating oil exceeds the set value of the PLC, the PLC will alarm and prompt, and the machine will stop to drain to prevent the lubricating oil from emulsification.

As shown in FIG. 3 , the first-stage oil-gas separation core in this embodiment supplies air to the second-stage body 20 through a gas supplement solenoid valve 35 and a one-way valve 13 . A check valve 16 and a check valve 21 are installed at the intake end and the exhaust end of the second-stage body 20 . The check valves 16 and 21 on both sides prevent air pressure recoil during operation, shutdown, and emergency stop, which will damage the first-stage compression system; at the same time, prevent the backflow of lubricating oil from the second-stage body 20, which may cause difficulty in secondary startup.

As shown in FIG. 3 , the dual-shaft motor 14 in this embodiment is controlled by a PLC33 frequency conversion. Further use multiple pressure and temperature sensors to detect the relevant signals of each section, and feedback the signals to the PLC to achieve multi-level protection functions and improve the safety performance of the compressor.

As shown in FIG. 3 , a pre-filter muffler box 37 is installed before a section of the air filter 8 in this embodiment. The pre-filter muffler box 37 is composed of a filter screen, a flame-retardant muffler cotton and a sheet metal cover, which can filter larger air in the air. particulate matter and reduce noise when venting.

As shown in Fig. 3, according to the setting operation sequence of Fig. 3, it is air → pre-filter muffler box 37 → intake filter 8 → integrated intake valve 7 → first-stage body 15 → first-stage oil and gas separation cylinder 1 → first-stage oil-gas separation core 2→First stage pressure maintenance valve 10→First stage air cooler 9→Mechanical water separator 30→Precision water separator 31→Check valve 16→Second stage body 20→Check valve 21→Second stage oil and gas separation cylinder 26→ Second-stage oil and gas separation core 27→Second-stage pressure maintenance valve 28→Second-stage gas cooler 29→Mechanical water separator 30→Customer.

When the method shown in Figure 4 is adopted, the sequence in operation is air → pre-filter muffler box 37 → intake filter 8 → integrated intake valve 7 → first stage body 15 → first stage oil and gas separation cylinder 1 → first stage oil and gas separation Core 2→first-stage pressure maintenance valve 10→first-stage air cooler 9→mechanical water separator 30→freeze dryer 34→precise air-water separator 31→check valve 16→second-stage body 20→check valve 21→ Second-stage oil and gas separation cylinder 26 → Second-stage oil and gas separation core 27 → Second-stage pressure maintenance valve 28 → Second-stage gas cooler 29 → Mechanical water separator 30 → Customer.

In this embodiment, the dual-shaft motor 14 is controlled by PLC33 to run slowly, and drives the first-stage body 15 and the second-stage body 20 simultaneously through the coupling. At this time, the integrated intake valve 7 is closed, its internal relief valve module is opened, and its internal loading solenoid valve is in a closed state; at the same time, the clean gas passes through the supplementary solenoid valve 35 and the one-way valve 13 pipeline to supplement the second-stage body 20. air to prevent the second-stage body 20 from being evacuated when it is just turned on. The normally closed solenoid valve 17 is closed. After running for the set time, the loading solenoid valve in the integrated intake valve 7 is energized, the relief valve module is closed, and the integrated intake valve 7 gradually opens until it is fully opened, turning into the loading mode. The air outside the box passes through the pre-filtering and muffler box 37, first coarsely filtered, and then enters the first section of the air filter 8 for filtration, and then enters the first section of the body 15 to compress the oil and gas in the first section of the body 15. Cyclone separation and one-stage oil and gas separation core 2 separate oil and gas.

After the compressed air gradually rises to the opening pressure of the pressure maintenance valve 10 with the internal pressure, the compressed air enters the first-stage air cooler 9, and after cooling, enters the mechanical air-water separator 30 and the precision water filter 31 one by one (also can be shown in Fig. 4 ). The compressed air after water removal enters the second-stage body 20 through the check valve 16 and is mixed with lubricating oil for compression, and the oil-gas mixture is discharged into the second-stage oil-gas separation cylinder 26 through the check valve 21 and separated by a mechanical cyclone And the second-stage oil and gas separation core 27 separates oil and gas. After the compressed air gradually rises to the opening pressure of the second-stage pressure maintenance valve 28 with the internal pressure, the compressed air enters the second-stage air cooler 29 and is separated by the mechanical water separator 30 before being supplied to the client.

During shutdown, the integrated intake valve 7 is fully closed, the relief valve module is fully opened, the loading solenoid valve in the integrated intake valve 7 loses power, and the first stage begins to discharge. At the same time, the discharge valve 18 acts to discharge, and the discharge pressure is reduced through the pressure reducing valve 12, and the discharge pressure is discharged into a section of oil and gas separator. The discharge speed can be adjusted by the moving ball valve.

The variable-frequency medium-pressure twin-screw air compressor of the utility model can compress air to 2.5-4.0 MPa, which meets the needs of different medium-pressure industries, and has the advantages of low cost, simple maintenance and stable performance.

Although the specific embodiments of the present invention are described above, those skilled in the art should understand that these are only examples, and the protection scope of the present invention is defined by the appended claims. Those skilled in the art can make various changes or modifications to these embodiments without departing from the principle and essence of the present invention, but these changes and modifications all fall within the protection scope of the present invention.

Claims (10)

1. An inverter-type medium-pressure twin-screw air compressor, characterized in that it comprises:

the double-output-shaft motor is a variable frequency motor;

the double-output-shaft motor is respectively connected with the first section of machine body and the second section of machine body and is in bidirectional transmission;

the first-stage cooling system is arranged between the first-stage engine body and the second-stage engine body and is used for cooling the compressed gas and the lubricating oil flowing from the first-stage engine body to the second-stage engine body;

and the water removal system is arranged between the first section of machine body and the second section of machine body and is used for drying the compressed gas and the lubricating oil which flow from the first section of machine body to the second section of machine body.

2. The inverter medium pressure twin screw air compressor of claim 1, wherein the primary cooling system is a primary air cooler.

3. The inverter medium pressure twin screw air compressor of claim 1, wherein the water removal system comprises, in order, a mechanical water separator and a precision water separator.

4. The variable frequency medium pressure twin screw air compressor of claim 1, wherein the water removal system comprises a mechanical water separator, a freeze dryer, and a precision gas-water separator in that order.

5. The variable-frequency medium-pressure twin-screw air compressor of claim 1, wherein the first section of the engine body is sequentially communicated with a first oil-gas separation cylinder, a first oil-gas separation core, a first pressure maintaining valve and the first section of the cooling system.

6. The variable-frequency medium-pressure twin-screw air compressor of claim 5, wherein the two-stage machine body is sequentially communicated with a two-stage oil-gas separation cylinder, a two-stage oil-gas separation core, a two-stage pressure maintaining valve and a two-stage air cooler.

7. The variable-frequency medium-pressure twin-screw air compressor according to claim 6, wherein an oil-water detector is installed at the bottom of the two-stage oil-gas separation cylinder.

8. The variable-frequency medium-pressure twin-screw air compressor of claim 5, wherein the first-stage gas-oil separation core supplies gas to the second-stage engine body through a gas supply solenoid valve and a check valve.

9. The variable frequency medium pressure twin screw air compressor of claim 1, wherein the two-stage block is fitted with check valves at both the inlet end and the outlet end.

10. The inverter medium pressure twin screw air compressor of any one of claims 1 to 9, wherein the twin output shaft motor is inverter controlled by a PLC.

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