CN111550939A - Variable working condition refrigeration cycle system and control method thereof - Google Patents
Variable working condition refrigeration cycle system and control method thereof Download PDFInfo
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- CN111550939A CN111550939A CN202010402943.2A CN202010402943A CN111550939A CN 111550939 A CN111550939 A CN 111550939A CN 202010402943 A CN202010402943 A CN 202010402943A CN 111550939 A CN111550939 A CN 111550939A
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- refrigeration cycle
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- 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- 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
- F25B41/37—Capillary tubes
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- 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
-
- G—PHYSICS
- G09—EDUCATION; CRYPTOGRAPHY; DISPLAY; ADVERTISING; SEALS
- G09B—EDUCATIONAL OR DEMONSTRATION APPLIANCES; APPLIANCES FOR TEACHING, OR COMMUNICATING WITH, THE BLIND, DEAF OR MUTE; MODELS; PLANETARIA; GLOBES; MAPS; DIAGRAMS
- G09B25/00—Models for purposes not provided for in G09B23/00, e.g. full-sized devices for demonstration purposes
- G09B25/02—Models for purposes not provided for in G09B23/00, e.g. full-sized devices for demonstration purposes of industrial processes; of machinery
Abstract
The invention relates to the technical field of refrigeration equipment and teaching equipment, in particular to a variable working condition refrigeration cycle system and a control method thereof, wherein the variable working condition refrigeration cycle system comprises a shell, a pipeline, a compressor, a condenser and an evaporator, wherein the pipeline is sequentially communicated with the compressor, the condenser and the evaporator to form a refrigeration loop, and the evaporator is arranged on the shell; further comprising: the variable working condition throttling device is arranged between the condenser and the evaporator; the refrigerant flow rate to the evaporator is adjusted, and the adjustment of the refrigeration working condition is realized; and a monitoring module for monitoring the state of the refrigeration circuit. The invention has the beneficial effects that: the structure is simple relatively, has practiced thrift equipment cost, through the variable operating mode throttling arrangement and the monitoring module that set up, can adjust the parameter under each operating mode, realizes the more intuitional understanding to refrigeration cycle, and then knows and study refrigeration cycle.
Description
Technical Field
The invention relates to the technical field of refrigeration equipment and teaching equipment, in particular to a variable working condition refrigeration cycle system and a control method thereof.
Background
With the development of the times, people have new requirements on the refrigeration industry, such as processing requirements of deep freezing and the like, and also have the desire of deepening research on a novel refrigeration theory, and in the development and progress of the refrigeration industry, people have deeper design and research on a refrigeration cycle system. How to use the refrigeration system of many loads variable operating mode to study refrigeration more directly to in the improvement current refrigerating plant, for example quick refrigeration, deep refrigeration. In college refrigeration education, a device is also needed to enable students to know about the refrigeration cycle and to have more intuitive knowledge of parameters under various working conditions.
In the prior art, the construction of a refrigeration system with multiple loads and variable working conditions is mostly assembled by adopting complete products on the market, the equipment cost is extremely high, the adjusting means is fixed, students cannot conveniently realize more visual understanding of the refrigeration cycle through parameter adjustment under each working condition, and then the refrigeration cycle is known and researched.
Disclosure of Invention
The invention aims to provide a variable working condition refrigeration cycle system and a control method thereof, which aim to solve the problems in the background technology.
In order to achieve the purpose, the invention provides the following technical scheme:
the utility model provides a change operating mode refrigeration cycle system, includes casing, pipeline, compressor, condenser and evaporimeter, the pipeline switches on in proper order compressor, condenser and evaporimeter form refrigeration circuit, the evaporimeter sets up on the casing, still include: the variable working condition throttling device is arranged between the condenser and the evaporator; the refrigerant flow rate to the evaporator is adjusted, and the adjustment of the refrigeration working condition is realized; and a monitoring module for monitoring the state of the refrigeration circuit.
As a further scheme of the invention: the variable working condition throttling device comprises capillary tubes and valve assemblies, wherein the capillary tubes are connected in parallel, and part or all of the capillary tubes are provided with the valve assemblies for controlling the on-off of the capillary tubes.
As a still further scheme of the invention: the inner diameter and the length of the capillary tube are set according to set sizes.
As a still further scheme of the invention: the monitoring module comprises a pressure gauge and a temperature monitor, and the two pressure gauges are respectively arranged at an air inlet and an air outlet of the compressor; the temperature monitor is disposed within the housing for monitoring an internal temperature of the housing.
As a still further scheme of the invention: the evaporator is a calandria evaporator.
As a still further scheme of the invention: and a support plate for supporting the shell is arranged in the shell.
As a still further scheme of the invention: the condenser is provided with a fan, and the fan is used for cooling the condenser.
As a still further scheme of the invention: the condenser is arranged on the top or the side of the shell through the fixing plate.
The invention provides another technical scheme that: a control method of a variable working condition refrigeration cycle system adopts any one of the variable working condition refrigeration cycle systems, and comprises the following specific steps:
the compressor is electrified, and the monitoring data of the monitoring module on the temperature and the pressure of the refrigeration loop are recorded;
and adjusting the flow of the refrigerant sent to the evaporator by the variable working condition throttling device for n times, and recording the temperature and pressure monitoring data of the refrigeration loop by the monitoring module after each adjustment.
As a further scheme of the invention: the n times are at least one time.
Compared with the prior art, the invention has the beneficial effects that: the structure is simple relatively, has practiced thrift equipment cost, through the variable operating mode throttling arrangement and the monitoring module that set up, can adjust the parameter under each operating mode, realizes the more intuitional understanding to refrigeration cycle, and then knows and study refrigeration cycle.
Drawings
Fig. 1 is a first working principle diagram of a variable working condition refrigeration cycle system.
Fig. 2 is a second working principle diagram of the variable working condition refrigeration cycle system.
Fig. 3 is an assembly schematic diagram of a variable condition refrigeration cycle system.
Fig. 4 is a schematic structural diagram of a housing in an embodiment of the invention.
Fig. 5 is a schematic structural diagram of a compressor according to an embodiment of the present invention.
Fig. 6 is a schematic structural view of an evaporator in an embodiment of the present invention.
Fig. 7 is a schematic structural diagram of a condenser in an embodiment of the present invention.
Fig. 8 is a schematic diagram of the system principle of the variable condition refrigeration cycle system.
In the drawings: 1-a compressor, 2-a condenser, 3-a capillary tube, 4-an evaporator, 5-a shell, 6-a pipeline, 7-a valve component, 8-a fan, 9-a thermometer and 10-a pressure gauge;
a0-b 0: an isentropic compression process in the compressor; b 0-c: isobaric cooling, condensing and supercooling in the condenser;
c-d 0: an isenthalpic throttling process within the throttle valve; d0-a 0: endothermic isobaric gasification process within the evaporator.
Detailed Description
Reference will now be made in detail to the exemplary embodiments, examples of which are illustrated in the accompanying drawings. When the following description refers to the accompanying drawings, like numbers in different drawings represent the same or similar elements unless otherwise indicated. The implementations described in the exemplary embodiments below are not intended to represent all implementations consistent with the present disclosure. Rather, they are merely examples of apparatus and methods consistent with certain aspects of the present disclosure, as detailed in the appended claims.
Referring to fig. 1-7, in an embodiment of the present invention, a variable-operating-condition refrigeration cycle system includes a casing 5, a pipeline 6, a compressor 1, a condenser 2, and an evaporator 4, where the pipeline 6 is sequentially connected to the compressor 1, the condenser 2, and the evaporator 4 to form a refrigeration loop, and the evaporator 4 is disposed on the casing 5, and further includes: the variable working condition throttling device is arranged between the condenser 2 and the evaporator 4; the evaporator is used for adjusting the flow of the refrigerant flowing to the evaporator 4 to realize the adjustment of the refrigeration working condition; and a monitoring module for monitoring the state of the refrigeration circuit.
Specifically, the refrigerant circulates compressor 1, condenser 2, variable working condition throttling arrangement and evaporimeter 4 in proper order, evaporimeter 4 is right the casing refrigerates. Changing the working condition of the refrigeration circuit by adjusting the flow of the refrigerant flowing through the variable working condition throttling device at regular time; the temperature in the box body is monitored through the monitoring module, and a temperature/menstruation change graph shown in figure 2 is drawn. Or, the monitoring module monitors the air pressure of the air inlet and the air outlet of the compressor, the pressure/length change chart shown in figure 1 is drawn, parameters under various working conditions are made into a chart, and the variable working condition refrigeration cycle system can be studied more intuitively.
In the embodiment of the invention, the refrigerant is R134a type refrigerant, is a pollution-free refrigerant, and is more environment-friendly compared with other refrigerants; the compressor is QD110h, the rated power is 240W, and the refrigerating capacity is 258W; the shell is made of abs plates and metal heat-insulation plates.
Referring to fig. 3, in the embodiment of the present invention, the variable working condition throttling device includes a capillary tube 3 and a valve assembly 7, the capillary tubes 3 are connected in parallel, and part or all of the capillary tubes 3 are provided with the valve assembly 7 for controlling the on-off of the capillary tubes 3; the inner diameter and the length of the capillary tube 3 are set according to set sizes.
Specifically, the capillary 3 is made of copper and is 1m, 2m and 3m respectively, the valve assembly comprises a first throttle valve, a second throttle valve and a third throttle valve, and the first throttle valve, the second throttle valve and the third throttle valve are arranged on the capillary 1m, the capillary 2m and the capillary 3m respectively, and multiple working conditions are adjusted.
When only 2m of capillary is on, the conditions are as follows: a0-b0 represents an isentropic compression process in a compressor; b0-c represents the isobaric cooling, condensing and supercooling process in the condenser; c-d0 represents an isenthalpic throttling process within the throttle valve; d0-a0 shows the endothermic isobaric gasification process within the evaporator.
When only 1m of capillary is on, the conditions are as follows: a1-b1 represents an isentropic compression process in a compressor; b1-c represents the isobaric cooling, condensing and supercooling process in the condenser; c-d1 represents an isenthalpic throttling process within the throttle valve; d1-a1 shows the endothermic isobaric gasification process within the evaporator.
When only 3m of capillary is on, the conditions are as follows: a2-b2 represents an isentropic compression process in a compressor; b2-c represents the isobaric cooling, condensing and supercooling process in the condenser; c-d2 represents an isenthalpic throttling process within the throttle valve; d2-a2 shows the endothermic isobaric gasification process within the evaporator.
Referring to fig. 3 and 8, in the embodiment of the present invention, the monitoring module includes a pressure meter and a temperature monitor, and the two pressures 10 are respectively disposed at an air inlet and an air outlet of the compressor 1; the temperature monitor is provided in the housing 5 for monitoring the internal temperature of the housing 5.
Specifically, the temperature monitor is a thermometer 9, the thermometer 9 is embedded on the shell, and the value of the thermometer can be observed from the outside; or a visual window is arranged on any surface of the shell relative to the thermometer 9, the difference value of the pressure gauge at the air inlet and the air outlet of the compressor 1 can be changed according to the on-off of different capillaries in the variable working condition throttling device, and the numerical value of the pressure gauge is recorded; recording the numerical change value of the inner thermometer 9 of the shell 5; and analyzing to obtain working effect graphs of the compressor, the condenser and the evaporator shown in figures 1 and 2 under various working conditions.
Referring to fig. 6, in the embodiment of the present invention, the evaporator is a calandria evaporator, and the calandria evaporator is formed by folding an S-shaped pipe in a reciprocating manner.
Specifically, the S-shaped reciprocating folding calandria evaporator is adopted, so that the heat dissipation area can be increased, and the working efficiency of the calandria evaporator is improved.
Referring to fig. 3 and 4, in the embodiment of the present invention, a supporting plate for supporting the housing is installed in the housing.
Specifically, at cryogenic in-process, the casing receives temperature variation to influence, takes place deformation, can reduce through the backup pad that sets up the deformation volume that the casing takes place, the protection casing.
Referring to fig. 3, in the embodiment of the present invention, a fan 8 is disposed on the condenser 2, and the fan 8 is used for cooling the condenser 2.
Specifically, condenser 2 is at the in-process of work, and the temperature risees, and its work efficiency descends, adopts fan 8 cool off condenser 2, guarantee condenser 2 is in stable, efficient operating condition.
Referring to fig. 3, in the embodiment of the present invention, the condenser 2 is disposed on the top or the side of the housing through the fixing plate.
Specifically, the condenser 2 is disposed at a side portion of the case through the fixing plate.
Preferably, the condenser 2 is disposed on the top of the housing 5 through the fixing plate, so that space can be saved.
Preferably, the condenser 2 and the compressor 1 are both arranged on the top of the shell 5 through the fixing plate, so that the space can be further saved.
In another embodiment provided by the invention, a method for controlling a variable working condition refrigeration cycle system adopts the variable working condition refrigeration cycle system, and comprises the following specific steps:
the compressor is electrified, and the monitoring data of the monitoring module on the temperature and the pressure of the refrigeration loop are recorded;
and adjusting the flow of the refrigerant sent to the evaporator by the variable working condition throttling device for n times, and recording the temperature and pressure monitoring data of the refrigeration loop by the monitoring module after each adjustment.
Specifically, the capillary 3 is made of copper and is 1m, 2m and 3m respectively, the valve assembly comprises a first throttle valve, a second throttle valve and a third throttle valve, the first throttle valve, the second throttle valve and the third throttle valve are mounted on the capillary of 1m, the capillary of 2m and the capillary of 3m respectively, and the control of three working conditions of the variable-working-condition refrigeration cycle system is realized by adjusting the first throttle valve, the second throttle valve and the third throttle valve once respectively.
The refrigerant is R-134a type refrigerant; the evaporator adopts a cooling calandria; the condenser is cooled by a fan; the compressor is QD110h, the rated power is 240W, and the refrigerating capacity is 258W; the shell is made of abs plates and metal heat-insulating plates.
Further, the n times are at least one time; and one of the first throttle valve, the second throttle valve and the third throttle valve is adjusted once to realize the control of one working condition of the variable working condition refrigeration cycle system.
The working principle of the invention is as follows: the refrigerant sequentially circulates the compressor 1, the condenser 2, the variable working condition throttling device and the evaporator 4, and the evaporator 4 refrigerates the shell; changing the working condition of the refrigeration circuit by adjusting the flow of the refrigerant flowing through the variable working condition throttling device at regular time; the temperature in the box body is monitored through the monitoring module, and a temperature/menstruation change graph shown in figure 2 is drawn. And/or monitoring the air pressure of an air inlet and an air outlet of the compressor through a monitoring module, drawing a pressure/length change diagram shown in figure 1, making parameters under various working conditions into a diagram, and visually studying and researching the variable-working-condition refrigeration cycle system by observing and analyzing the diagram.
As shown in fig. 1 and 2, the following are the pressure-enthalpy diagrams for the variable-condition refrigeration cycle system (lnP-h) And temperature entropy diagram (T-S) Detailed description of the drawings:
the method is divided into four stages:
d-a reactive constant voltage heat absorption; a-b adiabatic compression; b-c, releasing heat under the condition of reactive constant pressure; c-d adiabatic throttling.
c-d0-a0-b0 is a refrigeration cycle curve with the capillary length or the drift diameter being medium and equal;
c-d1-a1-b1 is the refrigeration cycle curve when the capillary length is longest or the path is narrowest;
c-d2-a2-b2 is the refrigeration cycle curve when the capillary length is shortest or the path is widest;
a2-b3 as a reference shows the reversible adiabatic compression process under ideal conditions.
When the condensation temperature and the condensation pressure are determined in advance by determining the high temperature environment (i.e., the bc-stage pressure is the same when changing conditions), when different capillaries are used:
in the case where the condensing pressure line is assumed to be constant and the degree of superheat is 0,
FIG. 1:
b-c in FIG. 1 are condensing pressure isobars d-a and evaporating pressure isobars a-b are adiabatic curves;
1. if the capillary tube is lengthened or the drift diameter is narrowed, the evaporation pressure is reduced (such as d1-a1 in figure 1), and the refrigerating capacity can be determined by the enthalpy difference between a1 and d1 in figure 1 (i.e., (h k =h a1 -h d1 ) It is shown that the capillary tube is stretched to make the refrigerating capacity small, the refrigeration is slow, only a proper amount of refrigerant is added, then the refrigerating effect can basically reach the requirement, after the external condition is determined, the adiabatic index is determined, when d1-a1 reaches the gas phase line, a1 is compressed to the isobaric line Pb of the condensing pressure according to a certain adiabatic index.
2. If the capillary tube is shortened or the diameter is widened, the more the refrigerant passes through, the higher the evaporation pressure (such as d2-a2 in figure 1), and the refrigerating capacity can be obtained by the difference between the enthalpy values of a2 and d2 in figure 1, namely (i)h k =h a2 -h d2 ) It is shown that shortening the capillary tube results in a large refrigeration capacity and faster refrigeration, and after the external conditions are determined, the adiabatic index is determined, and a2 is compressed to the isobar Pb of the condensing pressure according to a certain adiabatic index when d2-a2 reaches the gas phase line.
3. The pressure line (d 0-a 0) and the adiabatic curve (a 0-b 0) are between maximum and minimum with the capillary length or path centered.
FIG. 2:
b-c in FIG. 2 are the condensing pressure line d-a and the evaporating pressure line a-b, which are adiabatic curves;
1. if the length of the capillary tube is longer and the drift diameter is smaller, the flow rate of the refrigerant passing through the capillary tube is smaller, and the pressure is lower; according to the refrigerant thermodynamic properties, the lower the pressure, the lower the corresponding temperature, i.e., the lowest the d1-a1 line. At the gas phase line, the adiabatic exponent determined from the temperature and pressure reaches b1 through the adiabatic curve, and it is seen that the temperature is highest at b 1.
2. If the length of the capillary tube is shorter and the drift diameter is larger, the flow rate of the refrigerant passing through the capillary tube is larger, and the pressure is higher; according to the thermodynamic properties of the refrigerant, the higher the pressure, the higher the corresponding temperature, i.e., the highest in the d1-a1 line. At the gas phase line, the adiabatic exponent determined from the temperature and pressure reaches b2 through the adiabatic curve, and the temperature at b1 is the lowest as can be seen from the graph.
3. As with FIG. 1, the capillary length or path is centered with both the pressure line (d 0-a 0) and the adiabatic curve (a 0-b 0) between maximum and minimum.
It should be noted that the pressure gauge and the thermometer used in the present invention are prior art applications, and those skilled in the art can implement the intended functions according to the related description, or implement the technical features required to be accomplished by the similar techniques, and will not be described in detail herein.
Other embodiments of the disclosure will be apparent to those skilled in the art from consideration of the specification and practice of the disclosure herein. This application is intended to cover any variations, uses, or adaptations of the disclosure following, in general, the principles of the disclosure and including such departures from the present disclosure as come within known or customary practice within the art to which the disclosure pertains. It is intended that the specification and examples be considered as exemplary only, with a true scope and spirit of the disclosure being indicated by the following claims.
It will be understood that the present disclosure is not limited to the precise arrangements described above and shown in the drawings and that various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.
Claims (10)
1. The utility model provides a change operating mode refrigeration cycle system, includes casing, pipeline, compressor, condenser and evaporimeter, the pipeline switches on in proper order compressor, condenser and evaporimeter form refrigeration circuit, the evaporimeter sets up on the casing, its characterized in that still includes: the variable working condition throttling device is arranged between the condenser and the evaporator; the refrigerant flow rate to the evaporator is adjusted, and the adjustment of the refrigeration working condition is realized; and a monitoring module for monitoring the state of the refrigeration circuit.
2. The variable working condition refrigeration cycle system according to claim 1, wherein the variable working condition throttling device comprises a capillary tube and a valve assembly, the capillary tubes are connected in parallel, and part or all of the capillary tubes are provided with the valve assembly for controlling the on-off of the capillary tubes.
3. The variable duty refrigeration cycle system of claim 2, wherein the inner diameter and length of said capillary tube are sized.
4. The variable working condition refrigeration cycle system according to claim 1, wherein the monitoring module comprises a pressure gauge and a temperature monitor, and the two pressure gauges are respectively arranged at an air inlet and an air outlet of the compressor; the temperature monitor is disposed within the housing for monitoring an internal temperature of the housing.
5. The variable-duty refrigeration cycle system of claim 1, wherein said evaporator is a calandria evaporator.
6. The variable operation refrigeration cycle system as claimed in claim 1, wherein a support plate for supporting the casing is installed in the casing.
7. The variable duty refrigeration cycle system of claim 1, wherein said condenser is provided with a fan for cooling said condenser.
8. The variable-duty refrigeration cycle system according to any one of claims 1 to 7, further comprising a fixed plate, wherein the condenser is disposed on the top or side of the housing through the fixed plate.
9. A control method of a variable working condition refrigeration cycle system is characterized in that the variable working condition refrigeration cycle system as claimed in any one of claims 1 to 8 is adopted, and the method comprises the following specific steps:
the compressor is electrified, and the monitoring data of the monitoring module on the temperature and the pressure of the refrigeration loop are recorded;
and adjusting the flow of the refrigerant sent to the evaporator by the variable working condition throttling device for n times, and recording the temperature and pressure monitoring data of the refrigeration loop by the monitoring module after each adjustment.
10. The control method of a variable operation refrigerant cycle system as set forth in claim 9, wherein said n times is at least one time.
Priority Applications (1)
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| CN202010402943.2A CN111550939A (en) | 2020-05-13 | 2020-05-13 | Variable working condition refrigeration cycle system and control method thereof |
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| CN202010402943.2A CN111550939A (en) | 2020-05-13 | 2020-05-13 | Variable working condition refrigeration cycle system and control method thereof |
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| JP2009264688A (en) * | 2008-04-28 | 2009-11-12 | Hitachi Ltd | Air conditioner for railway vehicle |
| CN202304238U (en) * | 2011-09-13 | 2012-07-04 | 合肥美菱股份有限公司 | Multi-capillary combination and single-evaporator frequency conversion air-cooled frostless refrigerator |
| CN103473979A (en) * | 2013-09-11 | 2013-12-25 | 广东交通职业技术学院 | Teaching practical training platform for air conditioner comprehensive performance test |
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| CN205536643U (en) * | 2016-04-27 | 2016-08-31 | 合肥美菱股份有限公司 | Frequency conversion refrigerator refrigerating system of variable flow |
| CN206892987U (en) * | 2017-05-05 | 2018-01-16 | 大连富士冰山自动售货机有限公司 | The automatic vending machine of in parallel with double storehouses and single storehouse cascade evaporation device cooling unit |
| CN107894068A (en) * | 2017-11-14 | 2018-04-10 | 宁波奥克斯电气股份有限公司 | A kind of running state of air conditioner adjusting method and device |
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2020
- 2020-05-13 CN CN202010402943.2A patent/CN111550939A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009264688A (en) * | 2008-04-28 | 2009-11-12 | Hitachi Ltd | Air conditioner for railway vehicle |
| CN202304238U (en) * | 2011-09-13 | 2012-07-04 | 合肥美菱股份有限公司 | Multi-capillary combination and single-evaporator frequency conversion air-cooled frostless refrigerator |
| CN103473979A (en) * | 2013-09-11 | 2013-12-25 | 广东交通职业技术学院 | Teaching practical training platform for air conditioner comprehensive performance test |
| CN204944000U (en) * | 2015-07-10 | 2016-01-06 | 合肥晶弘电器有限公司 | A kind of three capillary electric control refrigerator |
| CN105737460A (en) * | 2016-03-20 | 2016-07-06 | 浙江迪贝电气股份有限公司 | Household refrigerator multi-stage throttling refrigerating system |
| CN205536643U (en) * | 2016-04-27 | 2016-08-31 | 合肥美菱股份有限公司 | Frequency conversion refrigerator refrigerating system of variable flow |
| CN206892987U (en) * | 2017-05-05 | 2018-01-16 | 大连富士冰山自动售货机有限公司 | The automatic vending machine of in parallel with double storehouses and single storehouse cascade evaporation device cooling unit |
| CN107894068A (en) * | 2017-11-14 | 2018-04-10 | 宁波奥克斯电气股份有限公司 | A kind of running state of air conditioner adjusting method and device |
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Application publication date: 20200818 |