CN109059359B - Compressor and compressor refrigerating system - Google Patents
Compressor and compressor refrigerating system Download PDFInfo
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- CN109059359B CN109059359B CN201810898837.0A CN201810898837A CN109059359B CN 109059359 B CN109059359 B CN 109059359B CN 201810898837 A CN201810898837 A CN 201810898837A CN 109059359 B CN109059359 B CN 109059359B
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- exchange pipeline
- compressor
- refrigerant
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- 239000003507 refrigerant Substances 0.000 claims abstract description 168
- 239000007788 liquid Substances 0.000 claims abstract description 90
- 238000005057 refrigeration Methods 0.000 claims abstract description 21
- 230000001172 regenerating effect Effects 0.000 claims abstract description 9
- 230000000149 penetrating effect Effects 0.000 claims abstract description 6
- 230000008929 regeneration Effects 0.000 claims abstract description 4
- 238000011069 regeneration method Methods 0.000 claims abstract description 4
- 239000012530 fluid Substances 0.000 claims description 15
- 229910052751 metal Inorganic materials 0.000 claims description 11
- 239000002184 metal Substances 0.000 claims description 11
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 6
- 229910052802 copper Inorganic materials 0.000 claims description 6
- 239000010949 copper Substances 0.000 claims description 6
- 238000000034 method Methods 0.000 claims description 6
- 238000011084 recovery Methods 0.000 description 18
- 238000004781 supercooling Methods 0.000 description 8
- 238000000859 sublimation Methods 0.000 description 7
- 230000008022 sublimation Effects 0.000 description 7
- 239000002826 coolant Substances 0.000 description 6
- 238000010438 heat treatment Methods 0.000 description 6
- 238000010521 absorption reaction Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 229920006395 saturated elastomer Polymers 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- BQCADISMDOOEFD-UHFFFAOYSA-N Silver Chemical compound [Ag] BQCADISMDOOEFD-UHFFFAOYSA-N 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000002360 explosive Substances 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 229910052709 silver Inorganic materials 0.000 description 2
- 239000004332 silver Substances 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 230000003245 working effect Effects 0.000 description 1
Classifications
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- 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
- F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A compressor and compressor refrigeration system, the compressor comprising: the device comprises a compressor body and a heat regenerating device communicated with an air inlet of the compressor body. The heat regeneration device comprises a shell with a hollow cavity and a heat exchange pipeline which is arranged in the shell in a penetrating way and two ends of which are respectively positioned outside the shell. The two opposite ends of the shell are respectively provided with a liquid inlet and a liquid outlet. And two opposite ports are arranged on the heat exchange pipeline, one of the ports is communicated with the air inlet of the compressor body, the other port is an air outlet of the heat exchange pipeline, and the other port is an air inlet of the heat exchange pipeline. The volume of the heat exchange pipeline in the shell is V g The volume of the hollow cavity in the shell is V l At V l ＞1.3V g And when the refrigerant in the heat exchange pipeline exchanges heat with the refrigerant flowing between the hollow cavity in the shell and the outer wall of the heat exchange device, the liquid refrigerant in the heat exchange pipeline absorbs heat and sublimates, and the liquid impact phenomenon of the compressor is improved.
Description
Technical Field
The invention relates to the technical field of refrigeration systems, in particular to a compressor and a refrigeration system of the compressor.
Background
At present, a gas-liquid separator is arranged at the inlet of the compressor to separate liquid refrigerant entering the compressor, but when the used gas-liquid separator works, the separated liquid refrigerant can flow back to a refrigerating system of the refrigerant after reaching a certain volume, and certain inherent space is occupied to occupy certain refrigerant, so that the part of refrigerant can not flow back to the refrigerating cycle system of the refrigerant, and the utilization efficiency of the refrigerant is reduced. And many refrigerants used in compressors are inflammable and explosive, and if the refrigerants leak, the risk degree of casualties is extremely high, so that when the refrigerants are applied, the injection quantity is limited by the International Electrotechnical Commission (IEC). However, the reduction of the refrigerant filling amount causes serious degradation of the refrigeration performance of the compressor refrigeration system in the refrigeration process.
Disclosure of Invention
The invention provides a compressor, which is used for improving the liquid impact phenomenon of a compressor body.
The invention provides a compressor, which is applied to a refrigerating system of the compressor and comprises a compressor body and a heat regenerating device communicated with an air inlet of the compressor body. The heat regeneration device comprises a shell with a hollow cavity and a heat exchange pipeline which is penetrated in the shell and two ends of which are respectively positioned outside the shell. The two opposite ends of the shell are respectively provided with a liquid inlet and a liquid outlet. And two opposite ports are arranged on the heat exchange pipeline, one of the ports is communicated with the air inlet of the compressor body, the other port is an air outlet of the heat exchange pipeline, and the other port is an air inlet of the heat exchange pipeline. When the gaseous refrigerant circulates from the heat exchange pipeline, heat exchange can be carried out between the fluid flowing between the hollow cavity in the shell and the outer wall of the heat exchange pipeline and the gaseous refrigerant in the heat exchange pipeline through the pipe wall of the heat exchange pipeline due to the existence of temperature difference between the fluid between the hollow cavity in the shell and the outer wall of the heat exchange pipeline.
The volume of the heat exchange pipeline in the shell is V g The volume of the hollow cavity in the shell is V l ，V l ＞1.3V g And when the liquid refrigerant in the heat exchange pipeline can absorb heat and sublimate sufficiently, the refrigerant flowing into the compressor body through the heat exchange pipeline is a gaseous refrigerant. The refrigerant at the low temperature in the heat exchange pipeline is heated by passing normal temperature between the hollow cavity of the shell and the outer wall of the heat exchange pipeline, so that the liquid refrigerant flowing into the compressor body sublimates, and the liquid impact phenomenon of the compressor body is improved. And the working load of the compressor body is reduced and the working efficiency of the compressor is improved by heating the refrigerant flowing into the compressor bodyThe rate.
In order to improve the safety factor for preventing the liquid refrigerant from entering the compressor body, the liquid refrigerant is correspondingly determined as V l ≥1.4V g . Through the volume of the hollow cavity in the shell, under the condition that the volume of the heat exchange pipeline is unchanged, the volume between the hollow cavity in the shell and the outer wall of the heat exchange pipeline can be increased, and then the amount of normal-temperature and normal-pressure liquid refrigerant transferring heat to the refrigerant in the heat exchange pipeline is increased, the liquid refrigerant which is not sublimated in the heat exchange pipeline is ensured to be fully sublimated, and the refrigerant entering the compressor body is a gaseous refrigerant. In addition, in order to improve the cooling medium in the heat exchange pipeline to sufficiently cool the liquid cooling medium with normal temperature and high pressure in the hollow cavity of the heat exchange pipeline outer shell, the supercooling degree of the cooling medium is improved, and the cooling medium is cooled to V l Is limited to V l <1.84V g The liquid refrigerant with normal temperature and high pressure between the hollow cavity in the shell and the outer wall of the heat exchange pipeline can be sufficiently cooled.
To sum up, the volume V of the hollow cavity in the shell l Volume V between the heat exchange pipeline in the shell and the heat exchange pipeline g Satisfy 1.4V g ≤V l ≤1.84V g When the liquid refrigerant flows into the compressor body through the heat exchange pipeline, the liquid refrigerant can be fully sublimated; and the normal-temperature high-pressure liquid refrigerant flowing between the hollow cavity in the shell and the heat exchange pipeline can be sufficiently cooled, and the supercooling degree of the refrigerant is improved. Under the condition of reducing the refrigerant filling quantity, the refrigerating efficiency of the refrigerating system can be improved by improving the supercooling degree of the refrigerant.
When the flow direction of the refrigerant between the hollow cavity in the heat recovery device and the outer wall of the heat exchange pipeline and the flow direction of the refrigerant in the heat exchange pipeline are specifically set, the liquid inlet of the shell and the gas outlet of the heat exchange pipeline are positioned at the same end of the shell, so that the flow direction of the refrigerant in the heat exchange pipeline is opposite to the flow direction of the refrigerant between the hollow cavity in the shell and the outer wall of the heat exchange pipeline, and the heat exchange efficiency is improved.
The heat exchange pipeline can be designed into a spiral pipe, so that the refrigerant is fully contacted with the pipe wall of the heat exchange pipeline, the contact area of the refrigerant in the heat exchange pipeline and the refrigerant between the outer walls of the heat exchange pipeline in the hollow cavity is increased, and the heat exchange efficiency is increased.
The wall of the heat exchange pipeline can use a metal pipe wall, and the heat exchange efficiency is increased by utilizing the good heat conductivity of the metal pipe wall. The metal pipe wall is preferably selected from metal copper, so that the cost of the product can be reduced.
The inner pipe wall of the heat exchange pipe can be provided with a plurality of fins which are arranged in a spiral way, and a groove is formed between two fins which are adjacent up and down on the inner pipe wall of the heat exchange pipe. The contact area between the refrigerant in the heat exchange pipeline and the wall of the heat exchange pipeline is increased through the fins and the grooves on the inner wall of the heat exchange pipeline, so that the working efficiency of heat exchange is improved.
The outer pipe wall of the heat exchange pipe is also provided with a plurality of fins which are arranged in a spiral way, and a groove is formed between two fins which are adjacent up and down on the outer pipe wall of the heat exchange pipe. The heat exchange efficiency is improved by increasing the contact area between the refrigerant between the hollow cavity in the shell and the outer wall of the heat exchange pipeline.
In addition, the invention also provides a compressor refrigeration system which comprises the compressor, the condenser and the evaporator. When specifically setting up, the gas outlet of compressor body passes through the connecting pipe intercommunication with the air inlet of condenser, and the liquid outlet of condenser passes through the inlet intercommunication of connecting pipe and foretell casing, and the liquid outlet of foretell casing communicates with the air inlet of evaporimeter, and the air outlet of evaporimeter passes through the connecting pipe and communicates with the air inlet of foretell heat transfer pipeline, and the air outlet of foretell heat transfer pipeline communicates with the air inlet of compressor body. The devices are communicated through the connecting pipes to form a closed refrigerant flowing loop, so that a refrigerating system is formed. Obviously, if the low-temperature low-pressure liquid refrigerant flowing into the evaporator is not sufficiently evaporated, the liquid refrigerant flows into the compressor body together with the refrigerant evaporated into a gaseous state, so that a liquid impact phenomenon is generated. In the invention, the refrigerant flowing out of the evaporator flows into the compressor body through the heat exchange pipeline of the heat regenerative device. In the heat exchange pipeline, a temperature difference exists between a normal-temperature high-pressure liquid refrigerant flowing out of the condenser and flowing between the hollow cavity in the shell and the outer wall of the heat exchange pipeline and a low-temperature low-pressure gaseous refrigerant in the heat exchange pipeline, and then the normal-temperature high-pressure liquid refrigerant can transfer heat to the low-temperature low-pressure gaseous refrigerant in the heat exchange pipeline through the pipe wall of the heat exchange pipeline. The liquid refrigerant which flows out of the evaporator and is not sublimated and mixed in the gaseous refrigerant can accelerate heat absorption and sublimation to be the gaseous refrigerant in the heating process, so that the refrigerant entering the compressor body is the gaseous refrigerant. The temperature of the liquid refrigerant at the liquid inlet of the hollow cavity in the shell is higher than that of the refrigerant at the liquid outlet of the hollow cavity in the shell by cooling the low-temperature low-pressure gaseous refrigerant in the heat exchange pipeline. And then the heat absorbed by the unit refrigerant when evaporating in the evaporator can be improved, the refrigeration efficiency of the refrigerant and the supercooling degree of the refrigerant are improved, and the refrigeration efficiency in the refrigeration system is further improved. Under the condition of ensuring that the filling quantity of the refrigerant in the refrigerating system is reduced, the same refrigerating performance is achieved by improving the supercooling degree of the refrigerant.
In a specific refrigeration system, a throttle device is provided. The liquid outlet of the heat regeneration device is communicated with the liquid inlet of the throttling device, and the liquid outlet of the throttling device is communicated with the liquid inlet of the evaporator. The saturated high-pressure normal-temperature liquid refrigerant is converted into a saturated low-temperature low-pressure liquid refrigerant in the throttling device, so that the refrigerant flowing into the evaporator is fully evaporated and absorbed, and the refrigerating efficiency of the refrigerating system is improved.
Drawings
FIG. 1 is a schematic view of a compressor according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of a refrigeration system with the present compressor according to an embodiment of the present invention;
fig. 3 is a schematic diagram of a compressor structure when the heat exchange pipeline provided by the embodiment of the invention is a spiral pipe.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail below with reference to the accompanying drawings, and it is apparent that the described embodiments are only some embodiments of the present invention, not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The invention provides a compressor, which is applied to a compressor refrigeration system. The compressor comprises a compressor body and a heat regenerating device arranged at an air inlet of the compressor body. Specifically, referring to fig. 1, the compressor includes a compressor body 1 and a heat regenerating device 2, and the heat regenerating device 2 communicates with an intake port 11 of the compressor body 1. The heat returning device 2 includes a housing 21 having a hollow cavity and a heat exchanging pipe 22 penetrating the housing 21 and exposing both ends. The housing 21 includes a liquid inlet and a liquid outlet. And the heat exchange pipeline 22 is provided with two opposite ports, one port is communicated with the air inlet of the compressor body 1, the port is an air outlet of the heat exchange pipeline 22, and the other port is an air inlet of the heat exchange pipeline 22. When the gaseous refrigerant flows from the heat exchange pipeline 22, heat exchange can be performed between the fluid flowing in the hollow cavity in the shell 21 and the gaseous refrigerant in the heat exchange pipeline 22 through the pipe wall of the heat exchange pipeline 21 due to the existence of the temperature difference between the fluid in the hollow cavity in the shell 21 and the gaseous refrigerant in the heat exchange pipeline 22. When the temperature of the fluid flowing between the hollow cavity in the shell 21 and the outer wall of the heat exchange pipeline 22 is higher than the temperature of the gaseous refrigerant in the heat exchange pipeline 22, the gaseous refrigerant in the heat exchange pipeline 22 can be heated, and the liquid refrigerant mixed in the heat exchange pipeline 22 can absorb heat and sublimate into the gaseous refrigerant through the heating of the fluid with higher temperature flowing in the shell 21. Thereby reducing the inflow of liquid refrigerant into the compressor body 1 and improving the liquid impact phenomenon of the compressor body 1.
The volume of the heat exchange tube 22 in the housing 21 is V g The hollow cavity in the housing 21 has a volume V l Volume V between the hollow cavity in the housing 21 and the outer wall of the heat exchange tube 22 penetrating the housing 21 c Is V (V) l -V g . At V l ＞1.3V g I.e. V g <3.3V c At this time, the volume V of the normal-temperature high-pressure fluid flowing between the hollow cavity in the housing 21 and the outer wall of the heat exchange pipe 22 c By at least one ofVolume of V c The normal-temperature high-pressure refrigerant flowing in the space between the hollow cavity in the shell 21 and the outer wall of the heat exchange pipeline 22 heats the low-temperature low-pressure gaseous refrigerant in the heat exchange pipeline 22, so that the liquid refrigerant in the heat exchange pipeline 22 is subjected to sufficient heat absorption and sublimation, the refrigerant entering the compressor body 1 is the gaseous refrigerant, and the liquid impact phenomenon of the compressor body 1 is improved. And the working load of the compressor body 1 is reduced and the working efficiency of the compressor is improved by heating the refrigerant flowing into the compressor body 1.
Obviously, whether the liquid refrigerant in the heat exchange tube 22 undergoes sufficient endothermic sublimation is related not only to the volume of the hollow cavity in the housing 21 and the volume in the heat exchange tube 22, but also to the temperature difference between the fluid between the hollow cavity in the housing 21 and the outer wall of the heat exchange tube 22 and the refrigerant in the heat exchange tube 22, the length, the size, and other factors of the heat exchange tube 22. In order to fully improve the liquid impact phenomenon of the compressor body 1, the liquid refrigerant in the heat exchange pipeline 22 can fully absorb heat and sublimate, the refrigerant entering the compressor body 1 is a gaseous refrigerant, the volume of the hollow cavity in the shell 21 and the volume in the heat exchange pipeline 22 are further limited, and V is formed l ≥1.4V g . By increasing the volume V between the hollow cavity in the housing 21 and the outer wall of the heat exchange tube 22 penetrating the housing 21 c Volume V of hollow cavity in housing 21 l The amount of the normal-temperature high-pressure liquid refrigerant for heating the refrigerant in the heat exchange pipeline 22 is increased, the working effect of the heat recovery device 2 is further optimized, and the liquid impact phenomenon of the compressor body 1 is improved.
In addition, the limited length of the heat exchange tube 22, the limited caliber of the heat exchange tube 22 and the limited volume of the heat exchange tube 22 in the shell 21 result in the limited amount of the refrigerant in the heat exchange tube 22, so that the limited amount of the liquid refrigerant in the heat exchange tube 22 and the limited amount of heat required for the liquid refrigerant to absorb heat and sublimate. In order to make the refrigerant entering the compressor body 1 be a gaseous refrigerant and improve the working efficiency of the heat recovery device 2, V is formed by l <1.84V g . Combining the V l ≥1.4V g 1.4V is obtained g ≤V l <1.84V g Can be provided with V l ＝1.40V g 、V l ＝1.45V g 、V l ＝1.50V g 、V l ＝1.55V g 、V l ＝1.60V g 、V l ＝1.65V g 、V l ＝1.70V g 、V l ＝1.75V g 、V l ＝1.80V g . In the interval, the liquid refrigerant entering the compressor body 1 can be fully subjected to heat absorption sublimation, and the refrigerant entering the compressor body 1 is a gaseous refrigerant; but also can ensure the working efficiency of the heat recovery device 2, and the refrigerant with lower temperature in the heat exchange pipeline 22 can sufficiently cool the fluid flowing between the hollow cavity in the shell 21 and the outer wall of the heat exchange pipeline 22.
Obviously, the higher the heat exchange efficiency between the fluid in the space between the heat exchange pipe 22 in the heat regenerator 2 and the hollow cavity in the housing 21 and the outer wall of the heat exchange pipe 22 and the refrigerant in the heat exchange pipe 22, the higher the working efficiency of the heat regenerator 2. Referring to fig. 1, in a process of specifically setting the heat recovery device 2, in order to ensure heat recovery efficiency, the flow direction of the refrigerant in the heat recovery pipe 22 is opposite to the flow direction of the refrigerant in the hollow cavity of the casing 21 and the refrigerant in the heat recovery pipe 22, and specifically, the liquid inlet of the casing 21 and the air outlet of the heat recovery pipe 22 are located at the same end of the casing 21. The flow speed difference between the refrigerant in the heat exchange pipeline 22 and the hollow cavity in the shell 21 and the outer wall of the heat exchange pipeline 22 is quickened. The fluid which conducts heat with each small unit refrigerant in the heat exchange pipeline 22 is kept at a relatively constant temperature, and the temperature difference between the refrigerant in the heat exchange pipeline 22 and the refrigerant outside the heat exchange pipeline 22 is gradually enlarged in the process that the refrigerant flows from the air inlet to the air outlet of the heat exchange pipeline 22. The heat exchange efficiency between the refrigerant in the heat exchange pipeline 22 and the fluid outside the heat exchange pipeline 22 in the hollow cavity of the shell 21 is improved, and the working efficiency of the whole heat recovery device 2 is further improved.
The shape and length of the heat exchange tube 22 also have an effect on the efficiency of the operation of the regenerator 2. The longer the length of the heat exchange tube 22, the longer the time required for the refrigerant to flow from the inlet of the heat exchange tube 22 to flow from the outlet of the heat exchange tube 22 at the same flow rate. The liquid refrigerant in the heat exchange pipeline 22 is guaranteed to absorb heat and sublimate for a sufficient time. Referring to fig. 3, in a specific arrangement, the heat exchange tube 22 may be designed as a spiral tube, and the length of the heat exchange tube 22 is extended by a spiral rising spiral. Not only increases the contact area between the refrigerant in the heat exchange pipeline 22 and the refrigerant in the hollow cavity of the shell 21, but also prolongs the time of heat exchange of the refrigerant in the heat exchange pipeline 22. The fluid between the hollow cavity in the shell 21 and the outer wall of the heat exchange pipeline 22 and the refrigerant in the heat exchange pipeline 22 are guaranteed to perform sufficient heat exchange, and the heat exchange efficiency is improved. In addition to the spiral tube type heat exchange tube 22, other spiral tubes, even coil type and folding type heat exchange tube 22 are also provided in the embodiment of the invention. It should be understood that the embodiment of the present invention is presented with respect to a spiral tube, which is intended to be a reference, and not a limitation on the manner in which the heat exchange tube 22 is spirally formed.
When the heat exchange pipeline 22 is specifically arranged, the pipe wall of the heat exchange pipeline 22 is arranged to be a metal pipe wall, and the heat exchange efficiency is increased through the good heat conducting property of the metal pipe wall. When the metal pipe wall is specifically selected, a silver pipe wall, a copper pipe wall and an aluminum pipe wall can be selected. Considering the differences among different metals, the metal tube wall of the heat exchange tube 22 is preferably selected from copper tube walls in combination with other factors such as different metal heat conductivity, economy, easy processing and the like. The heat exchange efficiency can be improved by utilizing the good heat conduction property of the copper pipe wall, so that the working efficiency of the heat recovery device 2 is improved. And compared with metallic silver, the metallic copper has lower price, saves the production cost of the heat recovery device 2, and is beneficial to the wide application of the heat recovery device 2.
When a specific heat exchange pipeline 22 is arranged, a plurality of fins which are spirally arranged can be arranged on the inner pipe wall of the heat exchange pipeline 22, and grooves are formed between the upper and lower adjacent fins on the inner pipe wall of the heat exchange pipeline 22. The contact area between the refrigerant flowing into the heat exchange pipe 22 through the air inlet of the heat exchange pipe 22 and the pipe wall of the heat exchange pipe 22 is increased. And a plurality of fins and grooves which are spirally arranged on the inner wall of the heat exchange pipeline 22 can guide the flowing direction of the refrigerant, so that the refrigerant in the heat exchange pipeline 22 can circulate spirally along a plurality of fins and grooves which are spirally arranged on the inner wall of the heat exchange pipeline 22, the flowing speed of the refrigerant in the heat exchange pipeline 22 can be slowed down, and the refrigerant between the inner and outer parts of the pipe wall of the heat exchange pipeline 22 can perform full heat exchange through the pipe wall of the heat exchange pipeline 22. In addition, the cooling medium flowing in the heat exchange pipeline 22 can be turned over continuously through the plurality of fins which are arranged on the inner wall of the heat exchange pipeline 22 and the grooves formed between the fins which are arranged in a spiral manner and the upper and lower adjacent fins, so that cooling medium units in contact with the inner wall of the heat exchange pipeline 22 can be updated continuously. Thereby the refrigerant in the heat exchange pipeline 22 absorbs heat sufficiently, the heat exchange efficiency between the refrigerants is increased, and the working efficiency of the heat recovery device 2 is further improved.
When the heat exchange tube 22 of the heat recovery device 2 is specifically arranged, a plurality of fins which are spirally arranged can be arranged on the outer tube wall of the heat exchange tube 22, and grooves are formed between the upper adjacent fins and the lower adjacent fins. The heat exchange efficiency between the refrigerant inside and outside the heat exchange pipe 22 in the housing 21 can also be increased in the same principle as described above.
The invention also provides a compressor refrigeration system, which comprises the compressor, a condenser and an evaporator. When specifically set up, referring to fig. 2, the air outlet of the compressor body 1 is communicated with the air inlet of the condenser 3 through a connecting pipe, the liquid outlet of the condenser 3 is communicated with the liquid inlet of the above-mentioned shell 21 through a connecting pipe, the liquid outlet of the above-mentioned shell 21 is communicated with the air inlet of the evaporator 4, the air outlet of the evaporator 4 is communicated with the air inlet of the above-mentioned heat exchange pipeline 22 through a connecting pipe, and the air outlet of the above-mentioned heat exchange pipeline 22 is communicated with the air inlet of the compressor body 1. The devices are communicated through the connecting pipes to form a closed refrigerant flowing loop, so that a refrigerating system is formed. In the refrigeration system, a low-temperature low-pressure gaseous refrigerant flows into the compressor body 1 through the heat exchange pipe 22, is compressed by the compressor body 1 to become a high-temperature high-pressure gaseous refrigerant, flows out of the compressor body 1 into the condenser 3, is fully liquefied and released in the condenser 3 to become a normal-temperature high-pressure liquid refrigerant, and flows into a space between the hollow cavity of the shell 21 and the outer wall of the heat exchange pipe 22, and then flows into the evaporator 4 to evaporate and absorb heat. Obviously, if the low-temperature low-pressure liquid refrigerant flowing into the evaporator 4 is not sufficiently evaporated, the liquid refrigerant flows into the compressor body 1 together with the sublimated gaseous refrigerant, so that the liquid impact phenomenon of the compressor body is generated. In the present invention, the refrigerant flowing out of the evaporator 4 flows into the compressor body 1 through the heat exchange pipe 22 of the heat recovery device 2. A temperature difference exists between the normal-temperature high-pressure liquid refrigerant flowing out of the condenser 3 and flowing between the hollow cavity in the shell 21 and the outer wall of the heat exchange pipeline 22 and the low-temperature low-pressure gaseous refrigerant in the heat exchange pipeline 22, so that the normal-temperature high-pressure liquid refrigerant can transfer heat to the low-temperature low-pressure gaseous refrigerant in the heat exchange pipeline 22 through the pipe wall of the heat exchange pipeline 22. The liquid refrigerant flowing out of the evaporator 4 and mixed in the gaseous refrigerant without sublimation is heated to accelerate heat absorption and sublimation into the gaseous refrigerant, so that the refrigerant entering the compressor body 1 is the gaseous refrigerant. In the process of heating the gaseous refrigerant in the heat exchange pipeline 22 by the liquid refrigerant outside the hollow cavity heat exchange pipeline 22 in the shell 21, the low-temperature low-pressure gaseous refrigerant in the heat exchange pipeline 22 is also used for cooling the liquid refrigerant at normal temperature and normal pressure in the hollow cavity outside the heat exchange pipeline 22. The temperature of the liquid refrigerant at the liquid inlet of the hollow cavity in the shell 21 is higher than that of the refrigerant at the liquid outlet of the hollow cavity in the shell 21 by cooling the low-temperature low-pressure gaseous refrigerant in the heat exchange pipeline 22. And the heat absorbed by the unit refrigerant during sublimation in the evaporator 4 is improved, the refrigeration efficiency of the refrigerant and the supercooling degree of the refrigerant are improved, and the refrigeration efficiency in the refrigeration system is further improved. Under the condition of ensuring that the filling quantity of the refrigerant in the refrigerating system is reduced, the same refrigerating performance is achieved by improving the supercooling degree of the refrigerant.
In the above-described refrigeration system, with continued reference to fig. 2, a throttle device 5 is provided between the regenerative device 2 and the evaporator 4. The liquid outlet of the shell 21 in the heat recovery device 2 is communicated with the evaporator 4 through the throttling device 5. The saturated high-pressure normal-temperature liquid refrigerant is converted into a saturated low-temperature low-pressure liquid refrigerant in the throttling device 5, and meanwhile, the flow speed of the refrigerant flowing into the evaporator 4 is controlled, so that the refrigerant flowing into the evaporator 4 is fully evaporated and absorbed, and the refrigerating efficiency of the refrigerating system is further improved.
Through the above technical scheme, the heat recovery device 2 is arranged on the air inlet of the compressor body 1, and under the proportional relationship between the volume in the heat exchange pipeline 22 in the shell 21 and the volume of the hollow cavity in the shell 21, which is defined above, the liquid refrigerant can be reduced from entering the compressor body 1 by introducing the fluid with the temperature higher than the temperature of the refrigerant in the heat exchange pipeline 22 into the space between the hollow cavity in the shell 21 and the outer wall of the heat exchange pipeline 22, so that the liquid impact phenomenon of the compressor body 1 is improved. And the compressor and the components in the corresponding refrigerating system can be communicated into a refrigerating system, and the supercooling degree of the refrigerant is improved through the heat exchange of the refrigerant between the inside and the outside of the heat exchange pipeline 22 in the regenerative device 2, so that the refrigerating efficiency of the refrigerant is improved, and the problem that the refrigerating performance of the refrigerating system can still be ensured under the condition of limiting the filling amount of flammable and explosive refrigerant is solved.
It will be apparent to those skilled in the art that various modifications and variations can be made to the present invention without departing from the spirit or scope of the invention. Thus, it is intended that the present invention also include such modifications and alterations insofar as they come within the scope of the appended claims or the equivalents thereof.
Claims (10)
1. The compressor is characterized by comprising a compressor body and a heat regenerating device; wherein,
the heat regeneration device comprises a shell with a hollow cavity and a heat exchange pipeline;
wherein, two opposite ends of the shell are respectively provided with a liquid inlet and a liquid outlet;
the heat exchange pipeline is arranged in the shell in a penetrating way, two ends of the heat exchange pipeline are respectively positioned outside the shell, and one end of the heat exchange pipeline exposed out of the shell is communicated with the air inlet of the compressor body;
the volume of the heat exchange pipeline in the shell is V g The volume of the hollow cavity is V l The method comprises the steps of carrying out a first treatment on the surface of the Wherein the V is l ＞1.3V g ；
The volume V between the hollow cavity in the shell and the outer wall of the heat exchange pipeline penetrating the shell c Is V (V) l -V g ，V g <3.3V c The volume V of the normal-temperature high-pressure fluid flowing between the hollow cavity in the shell and the outer wall of the heat exchange pipeline c At volume V c The normal-temperature high-pressure refrigerant flowing in the space between the hollow cavity in the shell and the outer wall of the heat exchange pipeline heats the low-temperature low-pressure gaseous refrigerant in the heat exchange pipeline, so that the liquid refrigerant in the heat exchange pipeline fully absorbs heat and sublimates, and the refrigerant entering the compressor body is the gaseous refrigerant.
2. The compressor according to claim 1, characterized in that the volume V of the heat exchange duct g Volume V of the hollow cavity l The method meets the following conditions: 1.4V g ≤V l <1.84V g 。
3. The compressor of claim 2, wherein the opposite ends of the heat exchange pipeline are respectively provided with an air inlet and an air outlet, and the air outlet of the heat exchange pipeline is communicated with the air inlet of the compressor body;
the liquid inlet of the shell and the air outlet of the heat exchange pipeline are positioned at the same end of the shell.
4. A compressor as claimed in claim 3 wherein said heat exchange conduit is a spiral conduit.
5. The compressor of claim 4, wherein the wall of the heat exchange tube is a metal wall.
6. The compressor of claim 5, wherein the wall of the heat exchange tube is a copper wall.
7. A compressor according to any one of claims 1 to 6, wherein a plurality of helically arranged fins are provided on the inner wall of the heat exchange tube.
8. The compressor of claim 7, wherein a plurality of helically arranged fins are provided on an outer tube wall of the heat exchange tube.
9. A compressor refrigeration system comprising a condenser, an evaporator and a compressor as claimed in any one of claims 1 to 8;
the air outlet of the compressor body is communicated with the air inlet of the condenser, the liquid outlet of the condenser is communicated with the liquid inlet of the shell, the liquid outlet of the shell is communicated with the liquid inlet of the evaporator, and the air outlet of the evaporator is communicated with the other end of the shell, which is exposed out of the heat exchange pipeline.
10. The compressor refrigeration system of claim 9 further comprising a throttling device, wherein a liquid inlet of the throttling device is in communication with a liquid outlet of the housing, and wherein a liquid outlet of the throttling device is in communication with a liquid inlet of the evaporator.
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| CN109945326A (en) * | 2019-04-16 | 2019-06-28 | 珠海格力电器股份有限公司 | Outdoor unit, heat exchange system, control method of heat exchange system and air conditioner |
| CN111059615A (en) * | 2019-12-20 | 2020-04-24 | 青岛海尔空调电子有限公司 | Multi-split air conditioning system |
| CN115790004A (en) * | 2022-06-09 | 2023-03-14 | 合肥美的电冰箱有限公司 | Heat regenerator, gas return pipeline system, gas circuit heat regeneration method and refrigeration equipment |
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