CN212959283U - Closed circulation coupling device - Google Patents
Closed circulation coupling device Download PDFInfo
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- CN212959283U CN212959283U CN202022147753.9U CN202022147753U CN212959283U CN 212959283 U CN212959283 U CN 212959283U CN 202022147753 U CN202022147753 U CN 202022147753U CN 212959283 U CN212959283 U CN 212959283U
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Abstract
A closed-cycle coupled device, the device comprising: the compressor unit consists of a two-stage centrifugal compressor of a static pressure air suspension bearing directly driven by a high-speed motor and used for compressing air; the refrigerating system consists of a single or a plurality of centrifugal refrigerating unit units of the static pressure gas suspension bearing and provides a cold source for the device; the gas cooling system includes a single or multiple interstage gas coolers or final stage gas coolers that chill the compressed gas. The three systems are highly coupled, have multiple working conditions, high adaptability and low running noise, do not need a lubricating oil system, and are efficient and energy-saving.
Description
Technical Field
The utility model relates to a compression technology field, in particular to high-speed motor based on static pressure air supporting bearing directly drives device of centrifugal compressor, centrifugal cooling water set and gas cooler closed circulation coupling.
Background
In various industries such as steel, chemical industry, glass and the like, compressed gas is required to meet the process requirements. The conventional compression system usually has a motor or a steam turbine to drive a centrifugal compressor unit, is limited by the rotating speed of a driving machine and a rotating speed changing device, has limited compression rotating speeds at all levels and low compression efficiency; the consumption of the driving process is large, and the energy is wasted; the compression and drive system occupies a large area, the lubricating oil system is complex, and the number of fault points is large; the compressor and the driver have high noise; the primary investment and the engineering cost are high; the operation and maintenance work is heavy and the cost is high; the energy-saving rise space is very limited.
The gas cooler matched with the conventional compressor unit adopts normal-temperature water of about 30-33 ℃ supplied by a conventional circulating water system as a cold source, the limiting temperature of compressed gas entering the next stage is about 35-40 ℃ mostly, the isothermal efficiency is low, the efficiency of the whole unit is low, and the optimal working characteristics of the compressor cannot be exerted. The final stage exhaust temperature of the traditional centrifugal compressor is between 70 and 105 ℃ limited by the temperature of the water supply of the circulating water, and a final stage gas cooler is usually required to be arranged or a separate air cooling system is required to be configured. For example, in an air separation system, a huge air cooling system (comprising two towers, four water pumps, even a water chilling unit and the like) needs to be arranged to reach the temperature required by the process, and the system has the problems of high investment cost, increased energy consumption of the water pumps and the water chilling unit and the like.
Disclosure of Invention
An object of the utility model is to overcome the not enough of prior art existence, and provide a system efficiency excellence, energy-conserving high-efficient, the configuration is simple (no lubricating system and independent driving machine system) compact, area is little, the operation is maintained simply, unit operation noise is ultralow. The system improves the working state of the compressor unit, and the system starts from the overall high efficiency and energy conservation of the unit, makes full use of the maximum potential of each unit, performs flow organization design in a targeted manner, breaks through the limitations of single machine capability and efficiency, and more importantly improves the high efficiency, economy, pertinence, flexibility of expansion and convenience of maintenance of the whole system.
The utility model aims at accomplishing through following technical scheme, a high-speed motor directly drives device of centrifugal compressor, centrifugal refrigerating unit and gas cooler closed circulation coupling based on static pressure air supporting bearing, it includes at least: the compressor unit is composed of a two-stage centrifugal compressor of a static pressure air suspension bearing directly driven by a high-speed motor and used for compressing air; the refrigerating system consists of a single or a plurality of centrifugal refrigerating unit units of the static pressure gas suspension bearing and provides a cold source for the device; the gas cooling system includes a single or multiple interstage gas coolers or final stage gas coolers that chill the compressed gas.
Preferably, the method comprises the following steps: the compressor unit has at least two gas inlets and two gas outlets via pipes and valves. The gas outlet is connected by piping and valves to gas inlets of the interstage gas cooler and the final stage gas cooler of the gas cooling system, the gas inlets are connected by piping and valves to gas outlets of the interstage gas cooler of the gas cooling system, and an outlet of the final stage gas cooler discharges compressed gas by piping and valves. A refrigerant outlet of the refrigerator unit is connected to refrigerant inlets of the interstage gas cooler and the final gas cooler of the gas cooling system by a pipe and a valve, and a refrigerant inlet of the refrigerator unit is connected to refrigerant outlets of the interstage gas cooler and the final gas cooler of the gas cooling system by a pipe and a valve.
Preferably, the method comprises the following steps: the compressed gas can be compressed by one compressor unit, or can be compressed by a plurality of compressor units in series or in parallel or in series and parallel.
Preferably, the method comprises the following steps: the temperatures of the refrigeration media entering and exiting the plurality of refrigeration unit units may be the same or different.
Preferably, the method comprises the following steps: it is not necessary that the gas cooling system include the interstage gas cooler or the final stage gas cooler, and the gas cooling system may include only the interstage gas cooler or only the final stage gas cooler or only partially include the interstage gas cooler and the final stage gas cooler.
The utility model has the advantages that the device has wide operating condition range, low unit noise and excellent COP and IPLV performances; lubricating oil is not needed, so that the pollution of the lubricating oil to compressed gas is avoided, the complexity of the system is reduced, the performance and the reliability are improved, and the maintenance cost is reduced.
The utility model has the other advantage that the device's refrigerant circulates between refrigerating system and gas cooling system, receives external environment's influence for a short time, and the dirt coefficient is low, and the heat transfer is effectual, and the device is small.
Another advantage of the present invention is that the device can be skid mounted to reduce the on-site installation effort and installation time and installation costs.
Drawings
The details of the invention are described in detail below with the aid of embodiments shown in the schematic drawings. Wherein:
fig. 1 is a schematic diagram of an example of a system according to the present invention.
Fig. 2 is a schematic view of another variant of the system according to the invention.
Fig. 3 is a schematic view of another variant of the system according to the invention.
Fig. 4 is a schematic view of another variant of the system according to the invention.
Fig. 5 is a schematic view of another variant of the system according to the invention.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings: as shown in fig. 1-5, a high-speed motor direct-drive centrifugal compressor, centrifugal refrigerating unit and gas cooler closed circulation coupling device based on static pressure air bearing, it includes at least: the compressor unit 1 consists of one or more compressor units 11, and a single compressor unit 11 consists of two-stage centrifugal compressors 14-1 and 14-2 of a static pressure gas suspension bearing 13 directly driven by a high-speed motor 12 and is used for compressing gas; the refrigerating system 2 consists of a single or a plurality of centrifugal refrigerating unit units 21 of static pressure gas suspension bearings and provides a cold source for the device; the gas cooling system 3 comprises a single or multiple interstage gas coolers 31 or final stage gas coolers 32, which lower the temperature of the compressed gas.
The compressor unit 11 is shown with at least two gas inlets 41, 42 and two gas outlets 51, 52 via pipes and valves. The gas outlets 51, 52 are connected by means of pipes and valves to the gas inlets of the interstage gas cooler 31 and the final stage gas cooler 32 of the gas cooling system 3, the gas inlet 42 is connected by means of pipes and valves to the gas outlet of the interstage gas cooler 31 of the gas cooling system 3, and the outlet of the final stage gas cooler 32 discharges compressed gas by means of pipes and valves. The refrigerant medium outlet 61 of the refrigerator unit 21 connects the refrigerant medium inlets 611, 612 of the interstage gas cooler 31 and the final gas cooler 32 of the gas cooling system 3 by pipes and valves, and the refrigerant medium inlet 71 of the refrigerator unit 21 connects the refrigerant medium outlets 711, 712 of the interstage gas cooler 31 and the final gas cooler 32 of the gas cooling system 3 by pipes and valves.
The compressed gas may be compressed by one compressor unit 11, or may be compressed by a plurality of compressor units 11 in series, parallel, or both. The temperatures of the refrigerant media to and from the plurality of refrigeration unit units 21 may be the same or different.
It is not essential that the gas cooling system 3 include the interstage gas cooler 31 or the last stage gas cooler 32, and the gas cooling system 3 may include only the interstage gas cooler 31 or only the last stage gas cooler 32 or only partially include the interstage gas cooler 31 and the last stage gas cooler 32.
A closed cycle coupling method for a high-speed motor direct-drive centrifugal compressor, a centrifugal refrigerating unit and a gas cooler based on a static pressure air bearing comprises the following steps:
compressed gas enters the compressor unit 11 through the gas inlet 41 and is compressed by the centrifugal compressor 14-1 directly driven by the static pressure gas suspension bearing 13 directly driven by the high-speed motor 12, the compressed gas enters the interstage gas cooler 31 of the gas cooling system 3 through the outlet 51 for cooling, the cooled gas enters the compressor unit 11 through the gas inlet 42 and is further compressed by the centrifugal compressor 14-2 directly driven by the static pressure gas suspension bearing 13 directly driven by the high-speed motor 12, the compressed gas enters the final stage gas cooler 32 of the gas cooling system 3 through the outlet 52 for cooling again, and the cooled compressed gas is discharged. The centrifugal chiller unit 21 of the hydrostatic gas suspension bearing provides refrigeration to the refrigerant medium to lower the temperature of the refrigerant medium entering the chiller unit 21 and through piping and valves to the refrigerant medium inlets 611, 612 of the interstage gas cooler 31 and the final stage gas cooler 32 for cooling the compressed gas.
The driving motor of the centrifugal compressor and the centrifugal refrigerating unit is a high-speed permanent magnet motor of a static pressure air bearing.
Preferably, the method comprises the following steps: the temperature of the refrigeration medium entering the interstage gas cooler 31 and the final stage gas cooler 32 is preferably between-15 and-5 ℃, so that the temperature of the compressed gas entering the gas inlet 42 after passing through the intermediate gas cooler 31 is preferably between-10 and-10 ℃.
If a plurality of the compressor units 11 are compressed in series or in parallel plus series, the temperature of the refrigerant medium entering the interstage gas cooler 31 and the final stage gas cooler 32 is preferably between-15 ℃ and-5 ℃ so that the temperature of the compressed gas entering the gas inlet 42 after passing through the interstage gas cooler 31 and entering the compressed gas inlet 41 of the next compressor unit 11 after passing through the final stage gas cooler 32 is preferably between-10 ℃ and-10 ℃.
Example (b):
in the embodiment of fig. 1, compressed air (e.g., air) having a temperature of about 20 ℃ after passing through the air filter enters the compressor unit 11 through the air inlet 41, the centrifugal compressor 14-1 with an inlet adjusting device, which is directly driven by the static pressure air suspension bearing 13 directly driven by one high-speed permanent magnet motor 12, is compressed to about 0.22mpa, the compressed air enters the interstage air cooler 31 of the gas cooling system 3 through the outlet 51 to be cooled to about 8 ℃, the cooled air enters the compressor unit 11 through the air inlet 42 and is further compressed to about 0.4 mpa by the centrifugal compressor 14-2 directly driven by the static pressure air suspension bearing 13 directly driven by the high-speed permanent magnet motor 12, the compressed air enters the final stage gas cooler 32 of the gas cooling system 3 through the outlet 52 to be cooled to about 8 ℃ again, and the cooled compressed air is discharged. The centrifugal refrigerating unit 21 with the static pressure gas suspension bearing supplies cold energy to a refrigerating medium (such as chilled water), so that the temperature of the refrigerating medium (such as chilled water) entering the refrigerating unit 21 is reduced from 10 ℃ to about 5 ℃, the refrigerating medium enters refrigerating medium inlets 611 and 612 of the interstage gas cooler 31 and the final stage gas cooler 32 through pipelines and valves to be used for cooling compressed gas, and the refrigerating medium is heated by the compressed gas to about 10 ℃ and then returns to the refrigerating unit 21 through the pipelines and valves to be cooled.
In the embodiment of fig. 2, the compressed gas a after the compressed gas is compressed by the compressor unit 11a and cooled by the gas cooling system 3a enters the gas inlet 41b of the compressor unit 11b, and the compressed gas b after the compressed gas is further compressed by the compressor unit 11b and cooled by the gas cooling system 3b exits. In fig. 2, the refrigerant medium (e.g., chilled water) in the refrigerator group unit 21 is cooled from 10 ℃ to about 5 ℃ and introduced into the refrigerant medium inlets 611a, 611b, 612a, 612b of the interstage gas coolers 31a, 31b and the final stage gas coolers 32a, 32b through pipes and valves, respectively, to cool the compressed gas, and the refrigerant medium is heated to about 10 ℃ by the compressed gas and then returned to the refrigerator group unit 21 through the refrigerant medium outlets 711a, 711b, 712a, 712b of the interstage gas coolers 31a, 31b and the final stage gas coolers 32a, 32b to be cooled through pipes and valves.
In the embodiment of fig. 3, the refrigeration system 2 is comprised of 2 refrigeration unit units 21a and 21 b. Wherein the refrigerant medium cooled by the refrigerator unit 21a is used to cool the inter-stage gas coolers 31a and 31b and the final stage gas cooler 32a of the gas cooling system 3, and the refrigerant medium cooled by the refrigerator unit 21b is used to cool the inter-stage gas cooler 31c and the final stage gas coolers 32b and 32c of the gas cooling system 3. The refrigeration capacity of the refrigeration unit units 21a and 21b may be the same or different. The flow rate, inlet temperature, and outlet temperature of the refrigerant entering and exiting the refrigeration unit 21a may be the same or different than the refrigerant entering and exiting the refrigeration unit 21b, depending on the particular process requirements.
In the embodiment of fig. 4, the compressed gas is divided into two streams through the gas inlet 41, and enters the compressor units 11a1 and 11a2 through the gas inlets 41a1 and 41a2, respectively, the compressor units 11a1 and 11a2 work in parallel, the gas cooling systems 3a1 and 3a2 cool the compressed gas in parallel, the pressure of the compressed gas a1 is the same as that of the compressed gas a2, and the compressed gas a1 and the compressed gas a2 can be combined into one stream after coming out, or not combined. The refrigeration unit 21 provides refrigeration to the gas cooling systems 3a1 and 3(a2), respectively.
In the embodiment of fig. 5, the compressed gas is divided into two streams through the gas inlet 41, and enters the compressor units 11a1 and 11a2 through the gas inlets 41a1 and 41a2, respectively, the compressor units 11a1 and 11a2 work in parallel, the compressed gas a1 and the compressed gas a2 exit and are combined into one stream of gas, which enters the compressor unit 11b through the gas inlet 41(b), is further compressed through the compressor unit 11b, and exits the compressed gas b after being further cooled by the gas cooling system 3 (b). The gas cooling systems 3a1, 3a2, and 3b cool the compressed gas, respectively. The refrigeration unit 21 provides refrigeration to the gas cooling systems 3a1, 3a2, and 3b, respectively.
As shown in fig. 1 to 5, these examples are only preferred embodiments of the present invention, but the present invention is not limited to the specific examples described above. In some special cases, such as the interstage gas cooler 31 and the final stage gas cooler 32 of FIGS. 1-5, may not be provided if the discharge temperature of the uncooled compressed gas is already sufficient for the needs of the subsequent process flow.
Therefore, various modifications or optimizations made within the scope of the present invention are also within the scope of the present invention.
Claims (4)
1. A closed-cycle coupled device comprising at least: the refrigerating system consists of a single or a plurality of centrifugal refrigerating unit units of the static pressure gas suspension bearing, and provides a cold source for the device, and the gas cooling system comprises a single or a plurality of interstage gas coolers or a final stage gas cooler, and cools the compressed gas.
2. The closed-cycle coupled apparatus according to claim 1, wherein the compressor unit has at least two gas inlets and two gas outlets by pipes and valves, the gas outlets) connect the gas inlets of the interstage gas cooler and the final gas cooler of the gas cooling system by pipes and valves, the gas inlets connect the gas outlets of the interstage gas cooler of the gas cooling system by pipes and valves, the outlet of the final gas cooler discharges compressed gas by pipes and valves, the refrigerant outlet of the refrigerator unit connects the refrigerant inlets of the interstage gas cooler and the final gas cooler of the gas cooling system by pipes and valves, the refrigerant inlet of the refrigerator unit connects the refrigerant inlets of the interstage gas cooler and the final gas cooler of the gas cooling system by pipes and valves And (7) an outlet.
3. The closed cycle coupled plant of claim 1 or 2, wherein the compressor units compress in series or parallel plus series.
4. The closed cycle coupled plant of claim 1 or 2, wherein the interstage gas cooler or the final stage gas cooler is not required and the gas cooling system may comprise only the interstage gas cooler or only the final stage gas cooler or only partially the interstage gas cooler and the final stage gas cooler.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2020212750334 | 2020-07-02 | ||
| CN202021275033 | 2020-07-02 |
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| Publication Number | Publication Date |
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| CN212959283U true CN212959283U (en) | 2021-04-13 |
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| CN202022147753.9U Active CN212959283U (en) | 2020-07-02 | 2020-09-27 | Closed circulation coupling device |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112032112A (en) * | 2020-07-02 | 2020-12-04 | 杭州制氧机集团股份有限公司 | Closed cycle coupling device and using method thereof |
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- 2020-09-27 CN CN202022147753.9U patent/CN212959283U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112032112A (en) * | 2020-07-02 | 2020-12-04 | 杭州制氧机集团股份有限公司 | Closed cycle coupling device and using method thereof |
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Address after: 799 Xiangfu Road, Qingshanhu street, Lin'an District, Hangzhou City, Zhejiang Province Patentee after: Hang Yang Group Co.,Ltd. Address before: 799 Xiangfu Road, Qingshanhu street, Lin'an City, Hangzhou City, Zhejiang Province Patentee before: Hangzhou oxygen generator group Co.,Ltd. |