CN109974322B - Double-temperature-zone single-stage refrigerating system with expander - Google Patents
Double-temperature-zone single-stage refrigerating system with expander Download PDFInfo
- Publication number
- CN109974322B CN109974322B CN201910315024.9A CN201910315024A CN109974322B CN 109974322 B CN109974322 B CN 109974322B CN 201910315024 A CN201910315024 A CN 201910315024A CN 109974322 B CN109974322 B CN 109974322B
- Authority
- CN
- China
- Prior art keywords
- refrigerant
- evaporator
- expander
- refrigerant outlet
- temperature
- 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.)
- Active
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 175
- 238000005057 refrigeration Methods 0.000 claims abstract description 27
- 239000007788 liquid Substances 0.000 claims abstract description 16
- 238000004891 communication Methods 0.000 claims abstract description 6
- 238000003860 storage Methods 0.000 claims abstract description 5
- 238000001704 evaporation Methods 0.000 description 7
- 230000008020 evaporation Effects 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 3
- 230000009977 dual effect Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- 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
- F25B31/00—Compressor 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
- F25B41/00—Fluid-circulation 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
-
- 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
-
- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- 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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
-
- 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/06—Several compression cycles arranged in parallel
- F25B2400/061—Several compression cycles arranged in parallel the capacity of the first system being different from the second
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
The invention discloses a double-temperature zone single-stage refrigeration system with an expander, which comprises a main compressor, wherein a refrigerant outlet of the main compressor is communicated with a refrigerant inlet of a condenser; the refrigerant outlet of the condenser is communicated with the liquid supply inlet of the liquid storage device; a refrigerant outlet of the accumulator is respectively communicated with a first refrigerant inlet of the economizer and a refrigerant inlet of the second expansion valve; the first refrigerant outlet of the economizer is communicated with the refrigerant inlet of the first evaporator through a first expansion valve; the refrigerant outlet of the second expansion valve is communicated with the refrigerant inlet of the second evaporator; the refrigerant outlet of the first evaporator is respectively communicated with the refrigerant inlets of the linkage compressor and the main compressor; the refrigerant outlet of the second evaporator is in communication with the refrigerant inlets of the expander and the main compressor, respectively. The double-temperature-zone single-stage refrigerating system disclosed by the invention can improve the operation energy efficiency of the refrigerating system when one refrigerating system is used for refrigerating two different temperature zone spaces.
Description
Technical Field
The invention relates to the technical field of refrigeration systems, in particular to a double-temperature-zone single-stage refrigeration system with an expander.
Background
Currently, for refrigeration systems, in refrigeration applications, there are often locations with different temperature ranges (i.e., temperature ranges), for example, gao Wenku (i.e., a refrigerator with a temperature higher than 0 degrees) and a low-temperature refrigerator (i.e., a refrigerator with a temperature lower than-15 degrees), and in some cases, in order to improve the energy efficiency level of the refrigeration system, two sets of refrigeration system units are needed to respectively refrigerate the high-temperature and low-temperature refrigerators, but this will increase the input cost once; in some cases, in order to save initial investment cost, a set of refrigeration system is used to refrigerate the refrigerators in two different temperature areas, and in this case, although one investment cost is saved, the energy efficiency level of the refrigeration system is lower because the outlet of the high-temperature evaporator in the refrigeration system has secondary throttling.
Therefore, there is an urgent need to develop a technology that can cool two different temperature zone (i.e., dual temperature zone) spaces using one set of cooling system, thereby improving the operation energy efficiency of the cooling system.
Disclosure of Invention
Therefore, the invention aims to provide a double-temperature-zone single-stage refrigerating system with an expander, which can improve the operation energy efficiency of the refrigerating system when a set of refrigerating system is used for refrigerating two different temperature-zone (namely double-temperature-zone) spaces, is beneficial to wide application and has great production and practice significance.
To this end, the invention provides a double-temperature zone single-stage refrigeration system with an expander, comprising a main compressor, wherein the refrigerant outlet of the main compressor is communicated with the refrigerant inlet of a condenser;
the refrigerant outlet of the condenser is communicated with the liquid supply inlet of the liquid storage device;
a refrigerant outlet of the accumulator is respectively communicated with a first refrigerant inlet of the economizer and a refrigerant inlet of the second expansion valve;
the first refrigerant outlet of the economizer is communicated with the refrigerant inlet of the first evaporator through a first expansion valve;
a refrigerant outlet of the second expansion valve is communicated with a refrigerant inlet of the second evaporator;
the refrigerant outlet of the first evaporator is respectively communicated with the refrigerant inlet of the linkage compressor and the refrigerant inlet of the main compressor;
the refrigerant outlet of the second evaporator is respectively communicated with the refrigerant inlet of the expander and the refrigerant inlet of the main compressor.
The first evaporator and the second evaporator are respectively arranged in the refrigerating spaces of the two different temperature areas;
the refrigerating temperature required by the refrigerating space arranged in the first evaporator is lower than the refrigerating temperature required by the refrigerating space arranged in the second evaporator.
The first refrigerant inlet of the economizer is communicated with the second refrigerant inlet of the economizer through a pipeline which is sequentially provided with an economizer throttling path electromagnetic valve and an economizer expansion valve.
Wherein the second refrigerant outlet of the economizer is in communication with the refrigerant outlet of the second evaporator through a hollow connecting line.
Wherein, a linkage electromagnetic valve is arranged on a connecting pipeline between the refrigerant outlet of the first evaporator and the refrigerant inlet of the linkage compressor;
a first bypass solenoid valve is provided on a connection line between a refrigerant outlet of the first evaporator and a refrigerant inlet of the main compressor.
Wherein, the connecting pipeline between the refrigerant outlet of the second evaporator and the refrigerant inlet of the expander is provided with an expander electromagnetic valve;
a second bypass solenoid valve is provided on a connection line between a refrigerant outlet of the second evaporator and a refrigerant inlet of the main compressor.
The power output end of the expander is connected with the power input end of the linkage compressor.
The refrigerant outlet of the expander and the refrigerant outlet of the linkage compressor are converged through pipelines and then are communicated with the refrigerant inlet of the main compressor.
Compared with the prior art, the double-temperature-zone single-stage refrigerating system with the expander can improve the operation energy efficiency of the refrigerating system when one set of refrigerating system is used for refrigerating two different temperature zone (namely double temperature zone) spaces, is beneficial to wide application, and has great production practice significance.
Drawings
FIG. 1 is a schematic diagram of a liquid separation device in a dual temperature zone single stage refrigeration system with an expander according to the present invention;
in the figure: 1 is a main compressor, 2 is a condenser, 3 is a liquid reservoir, 4 is an economizer, and 5 is a first evaporator;
6 is a second evaporator, 8 is an expander, 7 is a linkage compressor, and 9 is an economizer throttling path electromagnetic valve;
10 is an economizer expansion valve, 11 is a first expansion valve, 12 is a second expansion valve, 13 is a linkage compressor electromagnetic valve, 14 is an expansion electromagnetic valve, 15 is a first bypass electromagnetic valve, and 16 is a second bypass electromagnetic valve.
Detailed Description
In order to better understand the aspects of the present invention, the present invention will be described in further detail with reference to the drawings and embodiments.
Referring to fig. 1, the present invention provides a dual temperature zone single stage refrigeration system with an expander, comprising a main compressor 1, the refrigerant outlet of the main compressor 1 being in communication with the refrigerant inlet of a condenser 2;
the refrigerant outlet of the condenser 2 is communicated with the liquid supply inlet of the liquid reservoir 3;
the refrigerant outlet of the accumulator 3 is respectively communicated with the first refrigerant inlet of the economizer 4 and the refrigerant inlet of the second expansion valve 12;
the first refrigerant outlet of the economizer 4 communicates with the refrigerant inlet of the first evaporator 5 (specifically, a low temperature evaporator) through a first expansion valve 11;
the refrigerant outlet of the second expansion valve 12 communicates with the refrigerant inlet of the second evaporator 6 (specifically, a high-temperature evaporator);
the refrigerant outlet of the first evaporator 5 is respectively communicated with the refrigerant inlet of the linkage compressor 7 and the refrigerant inlet of the main compressor 1;
the refrigerant outlet of the second evaporator 6 communicates with the refrigerant inlet of the expander 8 and the refrigerant inlet of the main compressor 1, respectively.
In the present invention, in particular, the first evaporator 5 (particularly, a low-temperature evaporator) and the second evaporator 6 (particularly, a high-temperature evaporator) are respectively disposed in the refrigerating spaces of two different temperature areas, wherein the refrigerating temperature required by the refrigerating space disposed in the first evaporator 5 is lower than the refrigerating temperature required by the refrigerating space disposed in the second evaporator 6. The method specifically comprises the following steps: the first evaporator 5 (specifically, a low temperature evaporator) is disposed in a hollow sealed low temperature refrigerator (i.e., a refrigerator having a refrigerator temperature of less than-15 degrees), and the second evaporator 6 (specifically, a high temperature evaporator) is disposed in a hollow sealed Gao Wenku (i.e., a refrigerator having a refrigerator temperature of more than 0 degrees).
In the present invention, the first refrigerant inlet of the economizer 4 is also communicated with the second refrigerant inlet of the economizer 4 through a pipeline provided with an economizer throttle solenoid valve 9 and an economizer expansion valve 10 in sequence.
In the present invention, the second refrigerant outlet of the economizer 4 is in communication with the refrigerant outlet of the second evaporator 6 through a hollow connecting line.
In the present invention, the pressure of the throttled refrigerant in the economizer expansion valve 10 is equal to the refrigerant pressure at the refrigerant outlet of the second evaporator (i.e., the high temperature evaporator) 6.
In the invention, a linkage compressor electromagnetic valve 13 is arranged on a connecting pipeline between a refrigerant outlet of the first evaporator 5 and a refrigerant inlet of the linkage compressor 7;
a first bypass solenoid valve 15 is provided in a connection line between the refrigerant outlet of the first evaporator 5 and the refrigerant inlet of the main compressor 1.
In the present invention, in particular, an expander electromagnetic valve 14 is provided on a connection line between a refrigerant outlet of the second evaporator 6 and a refrigerant inlet of the expander 8;
a second bypass solenoid valve 16 is provided in a connection line between the refrigerant outlet of the second evaporator 6 and the refrigerant inlet of the main compressor 1.
In the invention, the power output end of the expander 8 is connected with the power input end of the linkage compressor 7, and the expander 8 can expand and do work and rotate by utilizing the refrigerant gas output by the second evaporator 6, so as to drive the linkage compressor 7 to work.
In the present invention, the expander 8 is a conventional expander, and for example, a scroll expander described in patent application CN201610033139 may be used, but other scroll expanders are also possible. The main function of the expander 8 is to utilize the refrigerant at the outlet of the second evaporator 6 to expand and apply work to drive the linkage compressor 7 to operate. The linkage compressor 7 is various in form, and can be any existing compressor capable of performing linkage operation with the expander, for example, a Mitsubishi V73 series compressor can be selected, and the main function of the linkage compressor 7 is to compress refrigerant gas at the outlet of the first evaporator 5 under the driving of the expander 8. In particular, the connection scheme of the expander 8 and the linkage compressor 7 can adopt belt pulley connection or shaft coupling connection and the like.
In the present invention, the refrigerant outlet of the expander 8 and the refrigerant outlet of the compressor 7 are connected together by a pipeline and then connected to the refrigerant inlet of the main compressor 1.
In the present invention, in particular, the main compressor 1 may be a conventional compressor for a refrigeration system, for example, a variable-frequency compressor or a multi-machine parallel compressor may be used, which mainly functions as: for compressing the refrigerant gas of low temperature and low pressure into gas of high temperature and high pressure and then discharging into the condenser 2;
a condenser 2 for discharging heat of the high-temperature and high-pressure refrigerant gas into a medium such as air or water, and condensing the refrigerant gas, wherein the refrigerant liquid formed after condensation enters the liquid storage tank 3;
a receiver 3 for storing a refrigerant liquid; after flowing out from the refrigerant outlet of the liquid accumulator 3, the refrigerant is divided into two paths, wherein one path of refrigerant directly throttles through the second expansion valve 12 and then enters the second evaporator (namely the high-temperature evaporator) 6; the other path of refrigerant is throttled by a first expansion valve 11 and then enters a first evaporator (i.e. a low-temperature evaporator) 5 after being further supercooled by an economizer assembly (comprising an economizer 4, an economizer throttle path electromagnetic valve 9 and an economizer expansion valve 10, for example);
in the present invention, the evaporation pressure and evaporation temperature of the refrigerant in the second evaporator (i.e., high temperature evaporator) 6 are high, and only a high space temperature can be maintained, and the refrigerant in the second evaporator absorbs heat by evaporation and can cool Gao Wenku (i.e., a refrigerator with a refrigerator temperature higher than 0 ℃);
the evaporation pressure and evaporation temperature of the refrigerant in the first evaporator (i.e. low-temperature evaporator) 5 are lower, the refrigerant in the first evaporator absorbs heat through evaporation and can be used for maintaining lower space temperature, and the low-temperature warehouse (i.e. the refrigerator with the warehouse temperature lower than-15 ℃) can be refrigerated and cooled.
In the present invention, the first bypass solenoid valve 15 and the second bypass solenoid valve 16 may be common solenoid valves in the existing refrigeration system, and perform the function of conducting or closing the pipeline.
In the invention, the expander 8 utilizes the high-temperature high-pressure gas output by the refrigerant outlet of the second evaporator (i.e. the high-temperature evaporator) 6 to perform expansion work rotation, and further drives the linkage compressor 7 to compress the refrigerant gas flowing out of the refrigerant outlet of the first evaporator (i.e. the low-temperature evaporator) 5, thereby improving the pressure of the refrigerant gas.
In the present invention, it should be noted that, when the refrigerant entering the first evaporator (i.e., the low temperature evaporator) 5 needs to be supercooled, the refrigerant entering from the accumulator 3 is divided into two paths, one path of refrigerant passes through the economizer throttle solenoid valve 9 and is throttled by the economizer expansion valve 10, thereby manufacturing a low temperature environment, absorbing the heat of the other path of refrigerant which is not throttled, supercooling the refrigerant, and simultaneously evaporating the refrigerant into the outlet of the second evaporator (i.e., the high temperature evaporator) 6, and throttling the refrigerant by the first expansion valve 11, and then entering the first evaporator (i.e., the low temperature evaporator) 5;
for the present invention to be embodied, the economizer 4 is a heat exchanger that absorbs heat by throttling the refrigerant itself to subcool another portion of the refrigerant.
The economizer 4 is configured to re-cool the refrigerant liquid supplied to the first evaporator (i.e., the low-temperature evaporator) 5, and the cold source thereof is from a low-temperature low-pressure refrigerant formed by throttling the refrigerant.
For the present invention, when two different temperature areas (for example, including a high temperature warehouse and a low temperature warehouse) need to be cooled simultaneously, the second evaporator (i.e., a high temperature evaporator) 6 and the first evaporator (i.e., a low temperature evaporator) 5 need to operate simultaneously, the first bypass solenoid valve (i.e., a low temperature bypass solenoid valve) 15 and the second bypass solenoid valve (i.e., a high temperature bypass solenoid valve) 16 are closed, the linkage compressor solenoid valve 13 and the expander solenoid valve 14 are opened, the refrigerant flowing out of the second evaporator (i.e., a high temperature evaporator) 6 and the refrigerant on the throttle side of the economizer 4 enter the expander 8 after being mixed to a certain pressure, and drive the linkage compressor 7 to operate, so that the refrigerant pressure at the refrigerant outlet of the first evaporator (i.e., a low temperature evaporator) 5 is compressed to a pressure range consistent with the refrigerant pressure at the refrigerant outlet of the expander 8, and the refrigerant pressure at the outlet of the first evaporator (i.e., a low temperature evaporator) 5 is raised, so that the refrigerant pressure at the first evaporator (i.e., a low temperature evaporator) can be further raised to the refrigerant outlet of the refrigerant system after the first evaporator (i.e., a high temperature evaporator) and the refrigerant system is further raised in the temperature after the first evaporator and the refrigerant system is cooled by the high temperature.
The refrigerant pressure at the refrigerant outlet of the expander 8 is lower than the refrigerant outlet pressure of the second evaporator (i.e., high temperature evaporator) 6, but higher than the refrigerant pressure at the refrigerant outlet of the first evaporator (i.e., low temperature evaporator) 5;
for the present invention, when only Gao Wenku is required to be cooled, only the second evaporator (i.e., high temperature evaporator) 6 is operated, the second bypass solenoid valve (i.e., high temperature bypass solenoid valve) 16 is opened, the first bypass solenoid valve (i.e., low temperature bypass solenoid valve) 15, the expansion solenoid valve 14 and the linkage solenoid valve 13, and the refrigerant flowing out of the second evaporator (i.e., high temperature evaporator) directly enters the compressor 1, forming the whole refrigeration cycle.
For the present invention, when it is required to cool only the low temperature bank, only the first evaporator (i.e., low temperature evaporator) 5 is operated, the first bypass solenoid valve (i.e., low temperature bypass solenoid valve) 15 is opened, the second bypass solenoid valve (i.e., high temperature bypass solenoid valve) 16, the expander solenoid valve 14 and the linkage solenoid valve 13 are closed, and the refrigerant flowing out of the first evaporator (i.e., low temperature evaporator) 5 directly enters the compressor 1, forming the whole refrigeration cycle.
It should be noted that, for the dual-temperature-area single-stage refrigeration system with the expander provided by the invention, the high-temperature refrigerant flowing out of the outlet of the second evaporator (i.e. the high-temperature evaporator) can be effectively utilized by adding the expander, and the expansion of the high-temperature refrigerant is utilized to drive the refrigerant at the outlet of the first evaporator (i.e. the low-temperature evaporator) to be compressed, so that after the refrigerant at the inlet of the main compressor is mixed, the pressure is improved to a certain extent, thereby improving the pressure ratio of the high pressure and the low pressure of the main compressor in working, and improving the operation energy efficiency of the refrigeration system on the premise of adopting only one refrigeration system.
Therefore, compared with the traditional mode of carrying out ineffective throttling (namely secondary throttling) on the refrigerant at the outlet of the second evaporator (namely the high-temperature evaporator), the invention can effectively utilize the work generated by the high-temperature refrigerant during expansion and improve the pressure of the refrigerant at the inlet of the main compressor, thereby improving the operation energy efficiency of the whole quality system.
In addition, the refrigeration system provided by the invention can also meet the refrigeration requirement of a single temperature zone by adding a bypass way.
In summary, compared with the prior art, the double-temperature-zone single-stage refrigerating system with the expander provided by the invention can improve the operation energy efficiency of the refrigerating system when one refrigerating system is used for refrigerating two different temperature zone (namely double temperature zone) spaces, is beneficial to wide application, and has great production practice significance.
The foregoing is merely a preferred embodiment of the present invention and it should be noted that modifications and adaptations to those skilled in the art may be made without departing from the principles of the present invention, which are intended to be comprehended within the scope of the present invention.
Claims (5)
1. A double-temperature zone single-stage refrigeration system with an expander, which is characterized by comprising a main compressor (1), wherein a refrigerant outlet of the main compressor (1) is communicated with a refrigerant inlet of a condenser (2);
the refrigerant outlet of the condenser (2) is communicated with the liquid supply inlet of the liquid storage device (3);
a refrigerant outlet of the liquid storage device (3) is respectively communicated with a first refrigerant inlet of the economizer (4) and a refrigerant inlet of the second expansion valve (12);
the first refrigerant outlet of the economizer (4) is communicated with the refrigerant inlet of the first evaporator (5) through a first expansion valve (11);
a refrigerant outlet of the second expansion valve (12) is communicated with a refrigerant inlet of the second evaporator (6);
the refrigerant outlet of the first evaporator (5) is respectively communicated with the refrigerant inlet of the linkage compressor (7) and the refrigerant inlet of the main compressor (1);
a refrigerant outlet of the second evaporator (6) is respectively communicated with a refrigerant inlet of the expander (8) and a refrigerant inlet of the main compressor (1);
the first evaporator (5) and the second evaporator (6) are respectively arranged in the refrigerating spaces of two different temperature areas;
the refrigerating temperature required by the refrigerating space arranged on the first evaporator (5) is lower than the refrigerating temperature required by the refrigerating space arranged on the second evaporator (6);
the power output end of the expander (8) is connected with the power input end of the linkage compressor (7);
the refrigerant outlet of the expander (8) and the refrigerant outlet of the linkage compressor (7) are converged through a pipeline and then are communicated with the refrigerant inlet of the main compressor (1);
the expander (8) is used for driving the refrigerant at the refrigerant outlet of the first evaporator (5) to be compressed by utilizing the expansion of the high-temperature refrigerant flowing out of the refrigerant outlet of the second evaporator (6), so that the pressure of the refrigerant at the refrigerant inlet of the main compressor (1) is increased after the refrigerant is mixed, and the pressure ratio of the high pressure to the low pressure of the main compressor (1) in operation is improved.
2. A double-temperature zone single-stage refrigeration system with an expander as claimed in claim 1, wherein the first refrigerant inlet of the economizer (4) is also in communication with the second refrigerant inlet of the economizer (4) through a line provided in series with an economizer orifice solenoid valve (9) and an economizer expansion valve (10).
3. A double-temperature zone single-stage refrigeration system with an expander as claimed in claim 1, wherein the second refrigerant outlet of the economizer (4) is in communication with the refrigerant outlet of the second evaporator (6) through a hollow connecting line.
4. A double-temperature zone single-stage refrigeration system with an expander according to claim 1, characterized in that a compressor electromagnetic valve (13) is provided on the connection line between the refrigerant outlet of the first evaporator (5) and the refrigerant inlet of the ganged compressor (7);
a first bypass solenoid valve (15) is provided on a connection line between a refrigerant outlet of the first evaporator (5) and a refrigerant inlet of the main compressor (1).
5. A double-temperature zone single-stage refrigeration system with an expander as claimed in claim 1, wherein an expander electromagnetic valve (14) is provided on the connection line between the refrigerant outlet of the second evaporator (6) and the refrigerant inlet of the expander (8);
a second bypass solenoid valve (16) is provided in a connection line between a refrigerant outlet of the second evaporator (6) and a refrigerant inlet of the main compressor (1).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910315024.9A CN109974322B (en) | 2019-04-18 | 2019-04-18 | Double-temperature-zone single-stage refrigerating system with expander |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910315024.9A CN109974322B (en) | 2019-04-18 | 2019-04-18 | Double-temperature-zone single-stage refrigerating system with expander |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109974322A CN109974322A (en) | 2019-07-05 |
| CN109974322B true CN109974322B (en) | 2024-03-26 |
Family
ID=67085236
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910315024.9A Active CN109974322B (en) | 2019-04-18 | 2019-04-18 | Double-temperature-zone single-stage refrigerating system with expander |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109974322B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111609593B (en) * | 2020-04-24 | 2021-06-25 | 珠海格力电器股份有限公司 | Double-temperature air conditioning system, control method and air conditioner |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20030072476A (en) * | 2002-03-04 | 2003-09-15 | 엘지전선 주식회사 | Gas heat pump driven by refrigerant steam turbine |
| KR20130091438A (en) * | 2012-02-08 | 2013-08-19 | 주식회사 신안그린테크 | Apparatus for cooling and dehydrating, control method and refrigerant circulating method for the same |
| CN103398485A (en) * | 2013-08-07 | 2013-11-20 | 东南大学 | Steam compression refrigerating system device and supercooling method |
| CN103615824A (en) * | 2013-12-06 | 2014-03-05 | 东南大学常州研究院 | Method and device for obtaining cooling capacities of multiple temperature zones based on expansion work recycling drive |
| CN107364564A (en) * | 2017-07-21 | 2017-11-21 | 天津商业大学 | The absorption CO for cooperateing with auxiliary to be subcooled with thermoelectric cooling2Marine refrigeration system |
| CN210089174U (en) * | 2019-04-18 | 2020-02-18 | 天津商业大学 | Double-temperature-zone single-stage refrigerating system with expander |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4969648B2 (en) * | 2007-05-16 | 2012-07-04 | パナソニック株式会社 | Expander-integrated compressor and refrigeration cycle apparatus including the same |
-
2019
- 2019-04-18 CN CN201910315024.9A patent/CN109974322B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20030072476A (en) * | 2002-03-04 | 2003-09-15 | 엘지전선 주식회사 | Gas heat pump driven by refrigerant steam turbine |
| KR20130091438A (en) * | 2012-02-08 | 2013-08-19 | 주식회사 신안그린테크 | Apparatus for cooling and dehydrating, control method and refrigerant circulating method for the same |
| CN103398485A (en) * | 2013-08-07 | 2013-11-20 | 东南大学 | Steam compression refrigerating system device and supercooling method |
| CN103615824A (en) * | 2013-12-06 | 2014-03-05 | 东南大学常州研究院 | Method and device for obtaining cooling capacities of multiple temperature zones based on expansion work recycling drive |
| CN107364564A (en) * | 2017-07-21 | 2017-11-21 | 天津商业大学 | The absorption CO for cooperateing with auxiliary to be subcooled with thermoelectric cooling2Marine refrigeration system |
| CN210089174U (en) * | 2019-04-18 | 2020-02-18 | 天津商业大学 | Double-temperature-zone single-stage refrigerating system with expander |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109974322A (en) | 2019-07-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100529589C (en) | Small-sized throttle low temperature refrigerator circulating system with injector | |
| CN109737622B (en) | Two-stage auto-cascade low-temperature refrigeration cycle system and circulation method for enhancing efficiency of two-stage ejector | |
| CN108800393B (en) | Air conditioning system | |
| JP2014029237A (en) | Two-stage-compression heat pump system | |
| CN109974322B (en) | Double-temperature-zone single-stage refrigerating system with expander | |
| CN108759139B (en) | Primary throttling intermediate incomplete cooling refrigeration system with intermediate temperature evaporator | |
| CN110608539A (en) | Cascade high-temperature heat pump system | |
| CN215002377U (en) | High-temperature gas heat pump unit adopting step heating | |
| CN111928512B (en) | Cold-hot combined multistage compression circulation system and control method | |
| CN210425610U (en) | Refrigeration system | |
| CN110411047B (en) | Refrigerating system | |
| JP2015102319A (en) | Refrigeration cycle device | |
| CN210089174U (en) | Double-temperature-zone single-stage refrigerating system with expander | |
| CN214791990U (en) | Multi-connected temperature-changing refrigeration house refrigeration system with single-stage and cascade circulation free conversion | |
| CN212157715U (en) | Injection supercharging step supercooling transcritical CO2System for controlling a power supply | |
| CN213873292U (en) | Novel throttling conversion device suitable for double cold source units | |
| CN210663485U (en) | Thermal fluorination defrosting system for refrigerating system and refrigerating system | |
| CN211233433U (en) | Double-air-supply heat pump system | |
| CN210861778U (en) | Super-cooled CO of non-azeotropic working medium supercharging machinery2Transcritical circulation refrigerating system | |
| CN109869945B (en) | Absorption type transcritical carbon dioxide double-stage compression refrigeration system | |
| CN102997527A (en) | Gas-liquid heat exchange type refrigeration device | |
| CN112880244A (en) | Two-phase flow air conditioning system with free cooling function | |
| CN110849032A (en) | Compressor waste heat driven compression-injection refrigerating system | |
| CN111141050B (en) | Injection supercharging cascade supercooling transcritical CO 2 System and application | |
| CN112629054A (en) | Multi-connected temperature-changing refrigeration house refrigeration system with single-stage and cascade circulation free conversion |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |