CN113482928A - Double-evaporation working condition, double-scroll compressor and air conditioning system - Google Patents
Double-evaporation working condition, double-scroll compressor and air conditioning system Download PDFInfo
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- CN113482928A CN113482928A CN202110935965.XA CN202110935965A CN113482928A CN 113482928 A CN113482928 A CN 113482928A CN 202110935965 A CN202110935965 A CN 202110935965A CN 113482928 A CN113482928 A CN 113482928A
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- 238000001704 evaporation Methods 0.000 title claims abstract description 20
- 238000004378 air conditioning Methods 0.000 title claims abstract description 18
- 230000000903 blocking effect Effects 0.000 claims abstract description 8
- 239000007788 liquid Substances 0.000 claims description 21
- 230000009977 dual effect Effects 0.000 claims 1
- 239000003507 refrigerant Substances 0.000 abstract description 33
- 230000008020 evaporation Effects 0.000 description 10
- 238000000034 method Methods 0.000 description 7
- 230000008569 process Effects 0.000 description 6
- 238000012545 processing Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000006872 improvement Effects 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000004888 barrier function Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000012938 design process Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Signal Processing (AREA)
- Mathematical Physics (AREA)
- Fuzzy Systems (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Rotary Pumps (AREA)
Abstract
The invention discloses a double-evaporation working condition double-scroll compressor and an air conditioning system, wherein the compressor comprises a shell, a driving motor is arranged in the shell, and the driving motor comprises a stator, a rotor and a shaft; a first movable scroll, a first fixed scroll, a second movable scroll and a second fixed scroll are sequentially arranged in the shell above the driving motor from bottom to top; a guide vane valve is arranged on the first fixed scroll; the shell is provided with a first low-pressure air inlet, a second low-pressure air inlet and a high-pressure air outlet; an oil blocking net is arranged in the shell above the second fixed scroll; a low-pressure cavity is formed between the driving motor and the first movable scroll plate, a medium-pressure cavity is formed between the first fixed scroll plate and the second movable scroll plate, and a high-pressure cavity is formed between the oil blocking net and the top of the shell; the refrigerating system can provide two kinds of refrigerants or secondary refrigerants with two parameters at the same time, reduces the operation cost on the premise of reducing the initial investment, improves the economic performance, saves energy and protects the environment.
Description
Technical Field
The invention belongs to the technical field of air conditioners, and particularly relates to a double-evaporation-condition double-scroll compressor and an air conditioning system.
Background
With the development of economy and society and the improvement of living standard of people, people have higher and higher requirements on the comfort in buildings. In the building indoor environment construction process, not only indoor air needs to be heated or cooled to meet indoor temperature requirements, but also fresh air needs to be conveyed to the interior of the building so as to meet the requirement of human bodies on air freshness. However, in the design process of the air conditioning system, outdoor fresh air generally needs to be cooled or heated before being sent to the indoor environment, so that the influence of the fresh air on the indoor temperature environment is reduced, and a fresh air processor is often required to be arranged to process the fresh air. At present, the same cold source is adopted in most buildings to process fresh air, namely, the same air conditioner host provides refrigerant or secondary refrigerant with the same parameter to process indoor air and fresh air, and the processing mode is simpler but not energy-saving. Because the temperature operating mode of new trend is generally more abominable than indoor temperature operating mode, use the high temperature cold source can handle the isenthalpic state point to indoor air with the new trend, and the evaporating temperature of cold source is higher, and coefficient of performance is higher, and is more energy-conserving. The other mode is to arrange two sets of air conditioner hosts, wherein one set of air conditioner hosts is specially used for treating indoor air, and the other set of air conditioner hosts is specially used for treating fresh air, so that the evaporation temperature of the set of air conditioner hosts for treating the fresh air can be increased, and the energy conservation in operation is realized. However, this method has a high initial cost and a complicated system.
Disclosure of Invention
The invention provides a double-evaporation working condition double-scroll compressor and an air conditioning system, aiming at solving the problems in the technical scheme of processing fresh air in the prior art, and realizing that the same refrigerating system simultaneously provides refrigerants or secondary refrigerants with two parameters so as to reduce the operation cost on the premise of reducing the initial investment.
The invention specifically comprises the following scheme:
the invention provides a double-evaporation working condition double-scroll compressor, which comprises a shell, wherein a driving motor is arranged in the shell, and the driving motor comprises a stator, a rotor and a shaft; a first movable scroll, a first fixed scroll, a second movable scroll and a second fixed scroll are sequentially arranged in the shell above the driving motor from bottom to top; a guide vane valve is arranged on the first fixed scroll; the shell is provided with a first low-pressure air inlet, a second low-pressure air inlet and a high-pressure air outlet; an oil blocking net is arranged in the shell above the second fixed scroll; the drive motor with constitute the low pressure chamber between the first vortex dish of moving, first certain vortex dish with constitute the middling pressure chamber between the second moves the vortex dish, oil blocking net with constitute the high pressure chamber between the casing top.
Preferably, the first low pressure inlet and the second low pressure inlet are located below the high pressure exhaust.
Preferably, the first low pressure inlet port is located below the second low pressure inlet port.
Preferably, the first low pressure inlet is provided in the side wall of the housing at the low pressure chamber.
Preferably, the second low pressure inlet is provided in the housing side wall of the medium pressure chamber.
Preferably, the high pressure exhaust port is provided on the housing side wall of the high pressure chamber.
The invention also provides an air conditioning system, which comprises the double-evaporation working condition, the double-scroll compressor, the gas-liquid separator, the air side heat exchanger, the fresh air heat exchanger and the indoor return air heat exchanger; the first low-pressure air inlet of the compressor is communicated and connected with the outlet of the gas-liquid separator, and the inlet of the gas-liquid separator is communicated and connected with the outlet of the indoor return air heat exchanger; the inlet of the wind side heat exchanger is communicated with the high-pressure exhaust port of the compressor; the second low-pressure air inlet of the compressor is communicated and connected with the outlet of the fresh air heat exchanger; and the outlet of the air side heat exchanger is respectively communicated and connected with the inlet of the indoor return air heat exchanger and the inlet of the fresh air heat exchanger.
Preferably, a first electronic expansion valve and a second electronic expansion valve are sequentially arranged on a pipeline which is communicated and connected with the outlet of the wind side heat exchanger and the inlet of the indoor return air heat exchanger.
Preferably, the first electronic expansion valve and the third electronic expansion valve are sequentially arranged on a pipeline which is communicated and connected with the outlet of the wind side heat exchanger and the inlet of the fresh air heat exchanger.
Preferably, the inlet of the wind side heat exchanger and the high-pressure exhaust port of the compressor, and the inlet of the gas-liquid separator and the outlet of the indoor return air heat exchanger are communicated and connected through a four-way valve.
The invention has the beneficial effects that:
the double-evaporation working condition, the double-scroll compressor and the air conditioning system can be connected with the heat exchangers under two different working conditions, so that two evaporation temperature working conditions are realized, the evaporation pressure of the evaporator for processing fresh air can be increased, and the double-scroll compressor and the air conditioning system have important energy-saving significance; the running mode of one compressor and two evaporation working conditions can be realized, the limiting situation that two compressors are required to be configured for realizing two evaporation working conditions in the prior art is changed, the same refrigerating system can provide two kinds of parameters of refrigerants or secondary refrigerants at the same time, the running cost is reduced on the premise of reducing the initial investment, the economic performance is improved, and the energy-saving and environment-friendly effects are realized.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic diagram of the dual-evaporation-condition, twin-scroll compressor of the present invention;
FIG. 2 is a schematic diagram of an air conditioning system according to the present invention;
the arrows in fig. 1 and 2 indicate the direction of refrigerant flow.
Fig. 3 is a refrigerant pressure-enthalpy diagram.
In fig. 1, 100 is a compressor, 1 is a housing, 2 is a stator, 3 is a rotor, 4 is a shaft, 5 is a first fixed scroll, 6 is a first fixed scroll, 601 is a vane valve, 7 is a second fixed scroll, 8 is a second fixed scroll, 9 is a first low-pressure air inlet, 10 is a second low-pressure air inlet, 11 is a high-pressure air outlet, 12 is an oil barrier, 13 is a low-pressure chamber, 14 is a medium-pressure chamber, 15 is a high-pressure chamber, 16 is an oil sump, 17 is a gas-liquid separator, 18 is a wind-side heat exchanger, 19 is a fresh air heat exchanger, 20 is an indoor return air heat exchanger, 21 is a first electronic expansion valve, 22 is a second electronic expansion valve, 23 is a third electronic expansion valve, and 24 is a four-way valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be clearly and completely described below with reference to the specific embodiments of the present invention and the accompanying drawings. It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The technical solutions provided by the embodiments of the present invention are described in detail below with reference to the accompanying drawings.
Example 1
As shown in fig. 1, the compressor includes a shell 1, a driving motor is arranged in the shell 1, and the driving motor includes a stator 2, a rotor 3 and a shaft 4; a first movable scroll 5, a first fixed scroll 6, a second movable scroll 7 and a second fixed scroll 8 are sequentially arranged in the shell 1 above the driving motor from bottom to top; a first low-pressure air inlet 9, a second low-pressure air inlet 10 and a high-pressure air outlet 11 are arranged on the shell 1; an oil blocking net 12 is arranged in the shell 1 above the second fixed scroll 8; a low-pressure cavity 13 is formed between the driving motor and the first movable scroll 5, a medium-pressure cavity 14 is formed between the first fixed scroll 6 and the second movable scroll 7, and a high-pressure cavity 15 is formed between the oil blocking net 12 and the top of the shell 1; the first fixed scroll 6 is provided with a vane valve 601.
As shown in fig. 1, it is further possible that the first low pressure inlet 9 and the second low pressure inlet 10 are located below the high pressure exhaust port 11.
As shown in fig. 1, it is still further possible that the first low pressure inlet 9 is located below the second low pressure inlet 10.
As shown in fig. 1, it is further possible that the first low pressure inlet 9 is provided on a side wall of the housing 1 at a low pressure chamber 13.
As shown in fig. 1, it is still further possible that the second low pressure inlet 10 is provided on the side wall of the casing 1 of the medium pressure chamber 14.
As shown in fig. 1, it is further possible that the high pressure exhaust port 11 is provided on the side wall of the housing 1 of the high pressure chamber 15.
As shown in fig. 1, an oil sump 17 is provided in the housing 1 below the shaft 4. The bottom of the shell 1 is provided with a base.
Example 2
As shown in fig. 2, an air conditioning system includes the dual-evaporation-condition, twin scroll compressor 100, the gas-liquid separator 17, the wind-side heat exchanger 18, the fresh air heat exchanger 19, and the indoor return air heat exchanger 20 according to any one of embodiment 1; the first low-pressure air inlet 9 of the compressor 100 is connected with the outlet of the gas-liquid separator 17 in a communicating manner, and the inlet of the gas-liquid separator 17 is connected with the outlet of the indoor return air heat exchanger 20 in a communicating manner; the inlet of the wind side heat exchanger 18 is communicated with the high pressure exhaust port 11 of the compressor 100; the second low-pressure air inlet 10 of the compressor 100 is connected with the outlet of the fresh air heat exchanger 19 in a communicating manner; and the outlet of the air side heat exchanger 18 is respectively communicated and connected with the inlet of the indoor return air heat exchanger 20 and the inlet of the fresh air heat exchanger 19.
As shown in fig. 2, a first electronic expansion valve 21 and a second electronic expansion valve 22 may be further provided in sequence on a pipeline connecting an outlet of the wind-side heat exchanger 18 and an inlet of the indoor return air heat exchanger 20.
As shown in fig. 2, the first electronic expansion valve 21 and the third electronic expansion valve 23 may be further disposed on a pipeline connecting the outlet of the wind-side heat exchanger 18 and the inlet of the fresh air heat exchanger 19 in a communicating manner.
As shown in fig. 2, the inlet of the wind-side heat exchanger 18 and the high-pressure outlet 11 of the compressor 100, and the inlet of the gas-liquid separator 17 and the outlet of the indoor return air heat exchanger 20 may be connected in communication by a four-way valve 24.
Above-mentioned two evaporation operating mode, two scroll compressor 100 and air conditioning system, the theory of operation is: the first-stage scroll comprises a first movable scroll 5 and a first fixed scroll 6, and the second-stage scroll comprises a second movable scroll 7 and a second fixed scroll 8; the refrigerant outlet of the indoor return air heat exchanger 20 is connected with the first low-pressure air inlet 9, the low-temperature low-pressure refrigerant gas from the indoor return air heat exchanger 20 enters the low-pressure cavity 13 of the compressor 100 through the first low-pressure air inlet 9, is compressed to the medium-pressure cavity 14 by the first-stage scroll, is mixed with the low-temperature medium-pressure refrigerant gas from the fresh air heat exchanger 19 and enters the medium-pressure cavity 14 from the second low-pressure air inlet 10, is continuously compressed into the high-temperature high-pressure refrigerant gas, is discharged from the high-pressure exhaust port 11 of the compressor 100 to the wind-side heat exchanger 18, is condensed and releases heat, and is changed into the low-temperature high-pressure refrigerant liquid. The refrigerant flowing out of the wind side heat exchanger 18 at the outdoor side is throttled by a first electronic expansion valve 21, is changed into low-temperature low-pressure refrigerant liquid and then is divided into two paths, one path of the refrigerant liquid enters a fresh air heat exchanger 19, absorbs fresh air heat, is evaporated into low-temperature medium-pressure refrigerant vapor and then enters a second low-pressure air inlet 10 of the compressor 100; the other path of refrigerant liquid is throttled into low-temperature low-pressure refrigerant liquid by the second electronic expansion valve 22, enters the indoor return air heat exchanger 20, is changed into low-temperature low-pressure refrigerant gas after absorbing indoor heat, and then enters the first low-pressure air inlet 9 of the compressor 100. Thus, two circulation loops are formed by continuous circulation.
Above-mentioned two evaporation operating mode, two scroll compressor and air conditioning system, refrigeration cycle's energy-conserving principle does: in the process of the refrigeration cycle, under the condition that other conditions are not changed, the evaporation temperature is increased, and the operation energy efficiency of the system is favorably improved. Because the temperature working conditions of the air treated by the indoor return air heat exchanger 20 and the fresh air heat exchanger 19 are different, wherein the indoor air treated by the indoor return air heat exchanger 20 is about 25 ℃, the outdoor air treated by the fresh air heat exchanger 19 is much worse than the indoor air in temperature working conditions, sometimes the outdoor temperature reaches 35 ℃ or even 40 ℃, so that the indoor air can be treated by a low-temperature refrigerant, and the fresh air can be treated by a medium-temperature refrigerant. Therefore, although the evaporation temperature of the refrigerant for processing the indoor air part is unchanged, the evaporation temperature of the refrigerant for processing the fresh air can be greatly increased, and the improvement of the whole operation efficiency is realized.
The pressure-enthalpy diagram of the specific refrigeration cycle of the double-evaporation working condition, the double-scroll compressor and the air conditioning system is shown in fig. 3, and the process is as follows: high-temperature and high-pressure refrigerant gas (state V) discharged by the compressor 100 is condensed and released heat in the air side heat exchanger 18 and is changed into a state VI (low-temperature and high-pressure liquid) from the state V, then the refrigerant gas is throttled to a state VII (low-temperature and medium-pressure liquid) through the first electronic expansion valve 21 and is divided into two paths, one path of the refrigerant gas enters the fresh air heat exchanger 19 to absorb heat of fresh air, the other path of the refrigerant gas is throttled to a state VIII (low-temperature and low-pressure liquid) through the second electronic expansion valve 22, and then the refrigerant gas enters the indoor return air heat exchanger 20 to treat indoor air. The refrigerant (state i) flowing out of the indoor return air heat exchanger 20 enters the first low pressure inlet 9 of the compressor 100, is compressed to state ii by the first stage scroll, is mixed with the refrigerant (state iii) from the fresh air heat exchanger 19 in the intermediate pressure chamber 14 of the compressor 100, and is compressed to state v by the second stage scroll of the compressor 100 after being changed to state iv.
The above description is only an example of the present application and is not intended to limit the present application. Various modifications and changes may occur to those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the scope of the claims of the present application.
Claims (10)
1. A double-evaporation working condition double-scroll compressor comprises a shell, wherein a driving motor is arranged in the shell and comprises a stator, a rotor and a shaft; the device is characterized in that a first movable scroll, a first fixed scroll, a second movable scroll and a second fixed scroll are sequentially arranged in the shell above the driving motor from bottom to top; a guide vane valve is arranged on the first fixed scroll; the shell is provided with a first low-pressure air inlet, a second low-pressure air inlet and a high-pressure air outlet; an oil blocking net is arranged in the shell above the second fixed scroll; the drive motor with constitute the low pressure chamber between the first vortex dish of moving, first certain vortex dish with constitute the middling pressure chamber between the second moves the vortex dish, oil blocking net with constitute the high pressure chamber between the casing top.
2. The dual-evaporation-mode, twin-scroll compressor of claim 1, wherein the first low-pressure inlet port and the second low-pressure inlet port are located below the high-pressure exhaust port.
3. The dual-evaporation-condition, twin-scroll compressor of claim 2, wherein the first low-pressure inlet port is located below the second low-pressure inlet port.
4. The dual-evaporation-condition, twin-scroll compressor of claim 3, wherein the first low-pressure inlet port is provided in the side wall of the housing at the low-pressure chamber.
5. The dual-evaporation-condition, twin-scroll compressor of claim 4, wherein the second low-pressure inlet port is provided in the shell sidewall of the intermediate-pressure chamber.
6. The dual-evaporation-condition, twin-scroll compressor of claim 5, wherein said high-pressure discharge port is provided in said shell side wall of said high-pressure chamber.
7. An air conditioning system comprising the dual evaporative condition, twin scroll compressor, gas liquid separator, wind side heat exchanger, fresh air heat exchanger and indoor return air heat exchanger of any one of claims 1 to 6; the first low-pressure air inlet of the compressor is communicated and connected with the outlet of the gas-liquid separator, and the inlet of the gas-liquid separator is communicated and connected with the outlet of the indoor return air heat exchanger; the inlet of the wind side heat exchanger is communicated with the high-pressure exhaust port of the compressor; the second low-pressure air inlet of the compressor is communicated and connected with the outlet of the fresh air heat exchanger; and the outlet of the air side heat exchanger is respectively communicated and connected with the inlet of the indoor return air heat exchanger and the inlet of the fresh air heat exchanger.
8. The air conditioning system as claimed in claim 7, wherein a first electronic expansion valve and a second electronic expansion valve are sequentially disposed on a pipeline connecting an outlet of said wind side heat exchanger and an inlet of said indoor return air heat exchanger.
9. The air conditioning system as claimed in claim 8, wherein the first electronic expansion valve and the third electronic expansion valve are sequentially disposed on a pipeline connecting the outlet of the wind side heat exchanger and the inlet of the fresh air heat exchanger.
10. The air conditioning system as claimed in claim 7, wherein the inlet of said wind side heat exchanger and said high pressure outlet of said compressor, and the inlet of said gas-liquid separator and the outlet of said indoor return air heat exchanger are connected by four-way valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110935965.XA CN113482928A (en) | 2021-08-16 | 2021-08-16 | Double-evaporation working condition, double-scroll compressor and air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110935965.XA CN113482928A (en) | 2021-08-16 | 2021-08-16 | Double-evaporation working condition, double-scroll compressor and air conditioning system |
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| CN113482928A true CN113482928A (en) | 2021-10-08 |
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|---|---|---|---|
| CN202110935965.XA Pending CN113482928A (en) | 2021-08-16 | 2021-08-16 | Double-evaporation working condition, double-scroll compressor and air conditioning system |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1335915A (en) * | 1998-10-13 | 2002-02-13 | 迈德技术公司 | Scroll-type fluid displacement device for vacuum pump application |
| JP2007198180A (en) * | 2006-01-24 | 2007-08-09 | Sanden Corp | Cold system |
| CN102425873A (en) * | 2011-11-16 | 2012-04-25 | 广州市设计院 | Method for preparing high/low temperature chilled water in single-machine twin-stage compression mode and special water chilling unit |
| DE102014117400A1 (en) * | 2014-11-27 | 2016-06-02 | Pfeiffer Vacuum Gmbh | Scroll vacuum pump |
| WO2018131111A1 (en) * | 2017-01-12 | 2018-07-19 | 三菱電機株式会社 | Multi-stage scroll compressor |
| KR20210050335A (en) * | 2019-10-28 | 2021-05-07 | 현대자동차주식회사 | Vehicle electric compressor system |
-
2021
- 2021-08-16 CN CN202110935965.XA patent/CN113482928A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1335915A (en) * | 1998-10-13 | 2002-02-13 | 迈德技术公司 | Scroll-type fluid displacement device for vacuum pump application |
| JP2007198180A (en) * | 2006-01-24 | 2007-08-09 | Sanden Corp | Cold system |
| CN102425873A (en) * | 2011-11-16 | 2012-04-25 | 广州市设计院 | Method for preparing high/low temperature chilled water in single-machine twin-stage compression mode and special water chilling unit |
| DE102014117400A1 (en) * | 2014-11-27 | 2016-06-02 | Pfeiffer Vacuum Gmbh | Scroll vacuum pump |
| WO2018131111A1 (en) * | 2017-01-12 | 2018-07-19 | 三菱電機株式会社 | Multi-stage scroll compressor |
| KR20210050335A (en) * | 2019-10-28 | 2021-05-07 | 현대자동차주식회사 | Vehicle electric compressor system |
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