CN104792051A - Multi-stage compression refrigerant circulation system and control method thereof - Google Patents
Multi-stage compression refrigerant circulation system and control method thereof Download PDFInfo
- Publication number
- CN104792051A CN104792051A CN201510160812.7A CN201510160812A CN104792051A CN 104792051 A CN104792051 A CN 104792051A CN 201510160812 A CN201510160812 A CN 201510160812A CN 104792051 A CN104792051 A CN 104792051A
- Authority
- CN
- China
- Prior art keywords
- compressor
- high stage
- stage compressor
- cold
- order
- 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.)
- Granted
Links
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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
Abstract
The invention provides a multi-stage compression refrigerant circulation system and a control method thereof. The multi-stage compression refrigerant circulation system comprises multiple stages of compressors, a condenser, a first throttling device and a first evaporator. A circulation loop is provided and used for enabling refrigerant to circulate sequentially among the stages of compressors, the condenser, the first throttling device and the first evaporator. The stages of compressors comprise the first-stage compressor and the second-stage compressor, the first-stage compressor and the second-stage compressor are compressors with different compressor mechanisms, the gas displacement of the first-stage compressor is larger than that of the second-stage compressor, the pressure difference of the second-stage compressor is larger than that of the first-stage compressor, the pressure difference is the difference between exhaust pressure and inlet pressure, and the second-stage compressor is connected to the exhaust side of the first-stage compressor.
Description
Technical field
The present invention relates to multiple compression refrigerant-cycle systems and control method thereof.
Background technology
Freezing unit usually can encounter high compression ratio, air-cooled heat pump producing high-temperature-hot-water, low ambient temperature also can encounter the requirement of high compression ratio when heating, solution is plural serial stage compressor, and current scheme adopts same compressor to connect.
Summary of the invention
One embodiment of the present of invention provide a kind of multiple compression refrigerant-cycle systems, comprise compound compressor, condenser, first throttle device and the first evaporimeter, and the closed circuit that cold-producing medium circulates successively between described compound compressor, described condenser, described first throttle device and described first evaporimeter is provided.Wherein this compound compressor comprises first order compressor and high stage compressor, described first and second stage compressors are the compressor with variety classes compressing mechanism, the capacity of first order compressor is greater than the capacity of high stage compressor, the pressure differential of high stage compressor is greater than the pressure differential of first order compressor, described pressure differential is the difference of pressure at expulsion and inlet pressure, and high stage compressor is connected to the exhaust side of first order compressor.
In a preferred embodiment, the described first order compressor of described multiple compression refrigerant-cycle systems is centrifugal compressor, and described high stage compressor is screw compressor.
In a preferred embodiment, the described first order compressor of described multiple compression refrigerant-cycle systems is screw compressor, and described high stage compressor is piston compressor or scroll compressor.
In a preferred embodiment, the described first order compressor of described multiple compression refrigerant-cycle systems and the first device in one-way on state are parallel to the suction side of described high stage compressor, and during to allow that described first order compressor quits work, cold-producing medium enters described high stage compressor through described first device in one-way on state.
In a preferred embodiment, the described high stage compressor of described multiple compression refrigerant-cycle systems and the second device in one-way on state are parallel to the exhaust side of described first order compressor, and during to allow that described high stage compressor quits work, cold-producing medium enters the downstream of described high stage compressor after first order compressor compresses through described second device in one-way on state.
In a preferred embodiment, the described high stage compressor of described multiple compression refrigerant-cycle systems and the second device in one-way on state are parallel to the exhaust side of described first order compressor, and during to allow that described high stage compressor quits work, cold-producing medium enters the downstream of described high stage compressor after first order compressor compresses through described second device in one-way on state.
In a preferred embodiment, the described compression-type refrigeration agent circulatory system of described multiple compression refrigerant-cycle systems also comprises economizer and the second throttling arrangement, the discharge opeing side of described condenser arranges first flow path through described economizer and the second stream, enters into described first flow path and described second stream respectively to make the condensate liquid exported from described condenser; Described second throttling arrangement is provided with in described second stream, described economizer allows the mutual heat exchange of cold-producing medium of described first flow path and described second stream, with make the cold-producing medium of described first flow path through described economizer carried out cold after enter described first throttle device again, and make the cold-producing medium of described second stream by after described second throttling arrangement throttling, evaporate through described economizer again, and then enter the upstream side of described high stage compressor.
In a preferred embodiment, the exhaust side of the described first order compressor of described multiple compression refrigerant-cycle systems arranges the 3rd stream being connected to described condenser, so that described condenser receives the exhaust exceeding the described first order compressor of described high stage compressor inspiratory capacity when the capacity of described first order compressor is greater than the inspiratory capacity of described high stage compressor; The downstream of described high stage compressor is provided with water heater and the 3rd throttling arrangement, described water heater be used for hot water preparing after the exhaust condensation of described high stage compressor, described 3rd throttling arrangement be used for through described water heater cold-producing medium throttling and be discharged into described condenser; Described condenser is used for be discharged into described first throttle device after the condensation of refrigerant of reception.
In a preferred embodiment, the described compression-type refrigeration agent circulatory system of described multiple compression refrigerant-cycle systems also comprises the second evaporimeter and the 4th throttling arrangement, the exhaust side of the second compressor arranges described condenser and first throttle device, described condenser is used for the exhaust of the second compressor described in condensation, described first throttle device is used for the cold-producing medium of condenser output described in throttling and is discharged into described first evaporimeter, described first evaporimeter has two exhaust sides, one of them exhaust side is communicated with described 4th throttling arrangement, described second evaporimeter be used for by through described 4th throttling arrangement condensation of refrigerant and be discharged into the suction side of described first order compressor, another exhaust side is wherein communicated with the suction side of described high stage compressor by the 4th stream, gaseous refrigerant can be supplemented to described high stage compressor by means of described 4th stream with the second evaporimeter described in making when the capacity of described first order compressor is less than the inspiratory capacity of described high stage compressor.
Another embodiment of the present invention also provides a kind of control method of multiple compression refrigerant-cycle systems, comprises the closed circuit providing cold-producing medium to circulate successively between compound compressor, condenser, first throttle device and the first evaporimeter.Wherein, the method also provides first order compressor and high stage compressor as described compound compressor, wherein said first and second stage compressors are the compressor with variety classes compressing mechanism, the capacity of first order compressor is greater than the capacity of high stage compressor, the pressure differential of high stage compressor is greater than the pressure differential of first order compressor, described pressure differential is the difference of pressure at expulsion and inlet pressure, high stage compressor is connected to the exhaust side of first order compressor;
Rated point mode of operation, medium and small load pattern, refrigeration originate mode, low-temperature heating pattern, supplying hot water pattern and/or ice-make mode are provided;
Wherein, in described rated point mode of operation, first order compressor is utilized to carry out supercharging to cold-producing medium, recycling high stage compressor carries out second compression again to described cold-producing medium, utilize condenser to the condensation of refrigerant of second compression again, divide two-way by condensed cold-producing medium, a road through economizer carried out cold after enter described first throttle device in described closed circuit, another road is evaporated through economizer, then enters described high stage compressor suction side;
At described medium and small load pattern, stop described first order compressor, only use described high stage compressor to carry out supercharging;
At described refrigeration originate mode, stop described high stage compressor, only use described first order compressor to cold-producing medium supercharging;
In described low-temperature heating pattern, on the basis of described rated point mode of operation, improve the supercharging multiple of first order compressor, high stage compressor;
In described supplying hot water pattern, the capacity of first order compressor is adjusted to the inspiratory capacity being greater than high stage compressor, first order compressor is utilized to carry out supercharging to cold-producing medium, cold-producing medium major part after supercharging is directly discharged to condenser, for refrigeration, utilize the second compressor to draw the exhaust of first order compressor remainder simultaneously, carry out second-compressed, the exhaust of the second compressor is discharged in water heater, obtain high-temperature water outlet, and carry out condensation by being discharged into described condenser after the cold-producing medium throttling of water heater further;
In described ice-make mode, the capacity of first order compressor is adjusted to the inspiratory capacity being less than high stage compressor, by the cold-producing medium after the compression of high stage compressor by condenser condenses, again by the throttling of first throttle device, cold-producing medium after throttling is evaporated by the first evaporimeter and divides two-way to export, a wherein road is turned back to the suction side of high stage compressor, will wherein after another route the 4th throttling arrangement throttling again by the second evaporator evaporation, then the suction side of first order compressor is turned back to, afterwards by the suction side being discharged to high stage compressor after first order compressor compresses, utilize cold-producing medium in the evaporation ice making of the second evaporimeter.
According to embodiments of the invention, in the occasion that gas transmission ability crosses, first order compressor adopts high gas transmission ability, high stage compressor increases progressively due to refrigerant density, volume flow diminishes and adopts gas transmission ability lower, simultaneously resistance to compression difference ability strengthens, and avoids the situation of the inefficiency of first order compressor under low discharge, large pressure reduction to occur like this.
Accompanying drawing explanation
The above and other features of the present invention, character and advantage become more obvious by passing through below in conjunction with the description of drawings and Examples, wherein:
Fig. 1 is the schematic diagram of compound compressor in one embodiment of the invention;
Fig. 2 is the schematic diagram of the refrigerant-cycle systems of the compound compressor comprised in Fig. 1;
Fig. 3 is the schematic diagram of compound compressor in another embodiment of the present invention;
Fig. 4 is the schematic diagram of compound compressor in yet another embodiment of the invention;
Fig. 5 is the schematic diagram of compound compressor in further embodiment of this invention;
Fig. 6 is the schematic diagram that the present invention goes back compound compressor in an embodiment;
Fig. 7 is the schematic diagram of another mode of operation embodiment illustrated in fig. 6;
Fig. 8 is the schematic diagram of another mode of operation embodiment illustrated in fig. 6;
Fig. 9 is for comprising the schematic diagram of the refrigerant-cycle systems of the compound compressor shown in Fig. 6;
Figure 10 is the schematic diagram of another refrigerant-cycle systems of the compound compressor comprised in Fig. 1;
Figure 11 is the schematic diagram of the another refrigerant-cycle systems of the compound compressor comprised in Fig. 1.
Detailed description of the invention
Below in conjunction with specific embodiments and the drawings, the invention will be further described; set forth more details in the following description so that fully understand the present invention; but the present invention obviously can implement with multiple this alternate manner described that is different from; those skilled in the art when doing similar popularization, deduction without prejudice to when intension of the present invention according to practical situations, therefore should can not limit the scope of the invention with the content of this specific embodiment.
Fig. 1 shows the combination of compound compressor in multiple compression refrigerant-cycle systems, first order compressor 11 and high stage compressor 12 are connected in series, namely high stage compressor 12 is arranged on the exhaust side of first order compressor 11, first order compressor 11 has different types of compressing mechanism relative to high stage compressor 12, there is stronger exhaust capacity, namely its capacity is greater than the capacity of high stage compressor 12, high stage compressor 12 has the poor ability of stronger resistance to compression relative to first order compressor 11, namely its pressure differential is greater than the pressure differential of first order compressor 11, described pressure differential is the difference of pressure at expulsion and inlet pressure.In a preferred embodiment, first order compressor 11 can be centrifugal compressor, high stage compressor 12 can be helical-lobe compressor, first, high stage compressor 11, 12 adjacent points, first order compressor 11 adopts centrifugal compressor can obtain large volume flow, high stage compressor 12 adopts helical-lobe compressor can obtain large pressure reduction, the compound compressor of centrifugal compressor is all adopted to combine relative to compound compressor, this preferred embodiment can avoid low discharge, the situation of the inefficiency of centrifugal compressor under large pressure reduction, centrifugal compressor, this combination of helical-lobe compressor adopts R134a to make cold-producing medium, be particularly suitable for ice storage system or air-cooled heat pump, or for producing the system of high-temperature-hot-water.In an additional preferred embodiment, first order compressor 11 can adopt helical-lobe compressor, high stage compressor 12 can adopt piston compressor or screw compressor, at first order compressor 11, point that high stage compressor 12 is adjacent, first order compressor 11 adopts screw compressor can obtain large volume flow; High stage compressor 12 adopts piston compressor or screw compressor can obtain large pressure reduction, the system of helical-lobe compressor is all adopted relative to compound compressor, this preferred embodiment can avoid the internal leakage situation of helical-lobe compressor under low discharge, large pressure reduction operating mode, this preferred embodiment adopts R410A, is particularly suitable for producing high-temperature-hot-water or ice storage system.
Fig. 2 shows an application refrigeration system embodiment illustrated in fig. 1, it comprises compound compressor 11, 12, condenser 2, first throttle device 3 and the first evaporimeter 4, and provide cold-producing medium at compound compressor 11, 12, condenser 2, the closed circuit circulated successively between first throttle device 3 and the first evaporimeter 4, economizer 5 and the second throttling arrangement 3A is also comprised in the downstream of the condenser 2 of this closed circuit, the discharge opeing side of condenser 2 arranges first flow path 51 through economizer 5 and the second stream 52, first flow path 51 and the second stream 52 is entered into respectively to make the condensate liquid exported from condenser 2.The second throttling arrangement 3A is provided with in second stream 52, economizer 5 allows the mutual heat exchange of cold-producing medium of first flow path 51 and the second stream 52, with make the cold-producing medium of first flow path 51 through economizer 5 carried out cold after enter first throttle device 3 again, and make the cold-producing medium of the second stream 52 by after the second throttling arrangement 3A throttling, evaporate through economizer 5 again, and then enter the upstream side of high stage compressor 12, high stage compressor 12 is entered into after mixing with the exhaust of first order compressor 11, the cold-producing medium be mixed into from the second stream 52 can play the effect of cooling protection to the cold-producing medium after first order compressor 11 increases, avoid the refrigerant temperature through high stage compressor 12 increase too high.
Fig. 3 shows the schematic diagram of compound compressor combination according to another embodiment of the present invention.Embodiment shown in Fig. 3 and other embodiment aftermentioned will continue to use element numbers and the partial content of previous embodiment, wherein adopt identical label to represent identical or approximate element, and optionally eliminate the explanation of constructed content.Explanation about clipped can refer to previous embodiment, repeats no more.With embodiment illustrated in fig. 1 unlike, first order compressor 11 and check valve 61 are connected in parallel on the suction side of high stage compressor 12, like this in some occasions, when only needing to provide low discharge cold-producing medium, can stop first order compressor 11, cold-producing medium enters into high stage compressor 12 from check valve 61 carry out supercharging with regard to direct.As long as first order compressor 11 is opened, because the exhaust lateral pressure of high stage compressor 11 is higher than suction side, therefore check valve 61 two-way stop.
Fig. 4 shows the schematic diagram according to compound compressor combination in one more embodiment of the present invention.With embodiment illustrated in fig. 1 unlike, high stage compressor 12 and check valve 62 are connected in parallel on the exhaust side of first order compressor 11, like this in some occasions, when only needing to provide large volume refrigerant flows, high stage compressor 12 can be stopped, increasing from first order compressor 11 rear refrigerant gas directly flow into high stage compressor 12 downstream from check valve 62.Similarly, as long as high stage compressor 12 is opened, because the exhaust lateral pressure of high stage compressor 12 is higher than suction side, therefore check valve 62 two-way stop.
Fig. 5 shows the schematic diagram of compound compressor combination according to still another embodiment of the invention.With embodiment illustrated in fig. 1 unlike, first order compressor 11 is in parallel with check valve 61, and high stage compressor 12 is in parallel with check valve 62, can provide more mode of operation like this to whole refrigerant system.As shown in Figure 7, in refrigerant-cycle systems under small load condition, when only needing to provide low discharge cold-producing medium, can stop first order compressor 11, cold-producing medium enters into high stage compressor 12 from check valve 61 carry out supercharging with regard to direct.As shown in Figure 8, when only needing to provide large volume refrigerant flows, high stage compressor 12 can be stopped, increasing from first order compressor 11 rear refrigerant gas directly flow into high stage compressor 12 downstream from check valve 62.As shown in Figure 6, after first order compressor 11, high stage compressor 12 are all opened, check valve 61,62 all two-way stops.
Be understandable that, the compound compressor combination shown in Fig. 1, Fig. 3 to Fig. 5, can be applied to the refrigerant-cycle systems shown in Fig. 2, Fig. 9, Figure 10 and Figure 11.When applying different compressor combination, different refrigerant-cycle systems can be adjusted slightly, only during stage compressor work, economizer can be cancelled or be equivalent to the heat exchanger of economizer.As shown in Figure 9, after the compressor combination shown in Fig. 5 being replaced the compressor combination in Fig. 2, a kind of refrigerant-cycle systems of more multi-operation mode can be obtained.Such as, in rated point mode of operation, first order compressor 11 pairs of cold-producing mediums are utilized to carry out supercharging, recycling high stage compressor 12 pairs of cold-producing mediums carry out second compression again, utilize condenser 2 to the condensation of refrigerant of second compression again, two-way is divided by condensed cold-producing medium, as previously shown, cold-producing medium in first flow path 51 through economizer 5 carried out cold after enter first throttle device 3, cold-producing medium in second stream 52 evaporates through economizer 5, enter high stage compressor 12 suction side again, in economizer 5, two-way cold-producing medium can carry out heat exchange again, cold-producing medium in second stream 52 can be issued additional, cold-producing medium in first flow path 51 can by excessively cold.For another example, medium and small load pattern can be provided, stop first order compressor 11, only use high stage compressor 12 to carry out supercharging.For another example, can be provided in refrigeration originate mode, stop high stage compressor 12, only use the 11 pairs of cold-producing medium superchargings of first order compressor.For another example, in low-temperature heating pattern, on the basis of described rated point mode of operation, the supercharging multiple of first order compressor 11, high stage compressor 12 can be improved.
Except the refrigeration system shown in Fig. 2 and Fig. 9, aforementioned compound compressor combination can also be used for obtaining higher condensation temperature, for hot water preparing.As shown in Figure 10, refrigerant-cycle systems comprises compound compressor, water heater 7, the 3rd throttling arrangement 3B, condenser 2, first throttle device 3, first evaporimeter 4, and compound compressor is wherein according to the combination configuration shown in Fig. 1.The exhaust side of first order compressor 11 is provided with the 3rd stream 53 being connected to condenser 2, so that condenser 53 receives the exhaust exceeding high stage compressor 12 inspiratory capacity when the capacity of first order compressor 11 is greater than the inspiratory capacity of high stage compressor 12.The downstream of high stage compressor 12 arranges water heater 7 and the 3rd throttling arrangement 3B, water heater 7 for hot water preparing after the exhaust condensation after high stage compressor 12 supercharging, the 3rd throttling arrangement 3B be used for through water heater 7 cold-producing medium throttling and be discharged into condenser 2.Condenser 2 for being discharged into first throttle device 3 by after the condensation of refrigerant of reception, and then turns back to the suction side of first order compressor 11 after the first evaporimeter 4 evaporates.While being freezed by the first evaporimeter 4 like this, higher condensation temperature can also be obtained by two stages of compression at water heater 7 place, thus for producing the hot water of higher temperature.
Figure 11 shows the another kind of application system of aforementioned compound compressor combination, and it may be used for ice making, and described ice making refers to that acquisition is equivalent to or subfreezing temperature, such as, produce frozen water or freezer occasion.Refrigerant-cycle systems shown in Figure 11 comprises compound compressor, condenser 2, first throttle device 3, condenser 2, first evaporimeter 4, the 4th throttling arrangement 3C, the second evaporimeter 4A, and compound compressor is wherein according to the combination configuration shown in Fig. 1.The exhaust side of the second compressor 12 arranges condenser 2 and first throttle device 3, condenser 2 is for the exhaust of condensation second compressor 12, the cold-producing medium that first throttle device 3 exports for throttling condenser 2 is also discharged into the first evaporimeter 4, first evaporimeter 4 has two exhaust sides, one of them exhaust side 42 is communicated with the 4th throttling arrangement 3C, second evaporimeter 4A be used for by through the 4th throttling arrangement 3C condensation of refrigerant and be discharged into the suction side of first order compressor 11, another exhaust side 41 is wherein communicated with the suction side of high stage compressor 12 by the 4th stream 54, gaseous refrigerant can be supplemented to high stage compressor 12 by means of the 4th stream 41 to make the second evaporimeter 4A when the capacity of first order compressor 11 is less than the inspiratory capacity of high stage compressor 12.Owing to entering the cold-producing medium of second time evaporimeter 4A via the 4th throttling arrangement 3C throttling again, therefore cold-producing medium has lower evaporating temperature at the second evaporimeter 4A relative to the first evaporimeter 4, utilizes the second evaporimeter 4A can produce frozen water or freezer occasion.
Fig. 9 to Figure 11 shows the different application of aforementioned compound compressor combination, be understandable that, these application systems can also be made in a refrigerant-cycle systems, according to aforementioned independently system or each autonomous system integrated after system, be appreciated that the control method according to multiple compression refrigerant-cycle systems of the present invention, comprise and provide cold-producing medium at compound compressor, condenser, the closed circuit circulated successively between first throttle device and the first evaporimeter, wherein, there is provided first order compressor and high stage compressor as described compound compressor, wherein first order compressor has stronger exhaust capacity relative to high stage compressor, high stage compressor has the poor ability of stronger resistance to compression relative to first order compressor, high stage compressor is connected to the exhaust side of first order compressor, this control method can provide rated point mode of operation, wherein, in described rated point mode of operation, first order compressor is utilized to carry out supercharging to cold-producing medium, recycling high stage compressor carries out second compression again to described cold-producing medium, utilize condenser to the condensation of refrigerant of second compression again, two-way is divided by condensed cold-producing medium, one tunnel through economizer carried out cold after enter described first throttle device in described closed circuit, another road is evaporated through economizer, then enters described high stage compressor suction side.
This control method can provide medium and small load pattern, wherein, at described medium and small load pattern, stops described first order compressor, only uses described high stage compressor to carry out supercharging.
This control method can provide refrigeration originate mode, wherein, at described refrigeration originate mode, stops described high stage compressor, only uses described first order compressor to cold-producing medium supercharging.
This control method can provide refrigeration originate mode, wherein, in described low-temperature heating pattern, on the basis of described rated point mode of operation, improves the supercharging multiple of first order compressor, high stage compressor;
This control method can provide supplying hot water pattern, wherein, in described supplying hot water pattern, the capacity of first order compressor is adjusted to the inspiratory capacity being greater than high stage compressor, first order compressor is utilized to carry out supercharging to cold-producing medium, cold-producing medium major part after supercharging is directly discharged to condenser, for refrigeration, utilize the second compressor to draw the exhaust of first order compressor remainder simultaneously, carry out second-compressed, the exhaust of the second compressor is discharged in water heater, obtain high-temperature water outlet, and carry out condensation by being discharged into described condenser after the cold-producing medium throttling of water heater further.
This control method can provide supplying hot water pattern, wherein, in described ice-make mode, the capacity of first order compressor is adjusted to the inspiratory capacity being less than high stage compressor, by the cold-producing medium after the compression of high stage compressor by condenser condenses, again by the throttling of first throttle device, cold-producing medium after throttling is evaporated by the first evaporimeter and divides two-way to export, a wherein road is turned back to the suction side of high stage compressor, will wherein after another route the 4th throttling arrangement throttling again by the second evaporator evaporation, then the suction side of first order compressor is turned back to, afterwards by the suction side being discharged to high stage compressor after first order compressor compresses, utilize cold-producing medium in the evaporation ice making of the second evaporimeter.
Aforementioned rated point mode of operation, medium and small load pattern, refrigeration originate mode, low-temperature heating pattern, supplying hot water pattern and/or ice-make mode go for same refrigerant-cycle systems, are applicable to different refrigerant-cycle systems respectively.
It should be noted that unless otherwise defined, otherwise all technical terms used in aforementioned description have understood identical implication usual with those of ordinary skill in the art.Describe ad hoc approach, device in subject application, but any method similar or of equal value with the method and apparatus described in foregoing teachings and material can use in the practice of this technology.Although quite in detail and by illustrating the embodiment of description technique, described explanation only for being expressly understood, and is not intended to limit.Use various term in the de-scription to pass on the understanding to this technology, should be understood that the implication of described various term extends to the common languages of various term or grammatical variants or form.Also should be understood that when term be finger device or equipment time, described term or name are referred to as the example in the present age and provide, and this technical step is by the restriction of described literal scope.Aforesaid term will be understood to by contemporary term description now, and described aforesaid term reasonably can be interpreted as the derivative of the system subset name that contemporary term or contemporary term comprise.In addition, when not departing from the scope of disclosed technology, any one or more features of any embodiment of technology can with any one or more other Feature Combinations of arbitrary embodiment of technology.Further, should understand, this technology is not limited to the embodiment of having set forth in order to illustration, but this technology only defines by the fair deciphering of present application for patent appended claims, comprises the equal authenticity of the gamut enjoyed of being had the right by each element of this technology.Therefore, although the present invention with preferred embodiment openly as above, it is not that any those skilled in the art without departing from the spirit and scope of the present invention, can make possible variation and amendment for limiting the present invention.Therefore, every content not departing from technical solution of the present invention, any amendment done above embodiment according to technical spirit of the present invention, equivalent variations and modification, all fall within protection domain that the claims in the present invention define.
Claims (10)
1. multiple compression refrigerant-cycle systems, comprise compound compressor, condenser, first throttle device and the first evaporimeter, and provide cold-producing medium at described compound compressor, described condenser, the closed circuit circulated successively between described first throttle device and described first evaporimeter, it is characterized in that described first and second stage compressors are the compressor with variety classes compressing mechanism, the capacity of described first order compressor is greater than the capacity of described high stage compressor, the pressure differential of described high stage compressor is greater than the pressure differential of described first order compressor, described pressure differential is the difference of pressure at expulsion and inlet pressure, described high stage compressor is connected to the exhaust side of described first order compressor.
2. multiple compression refrigerant-cycle systems as claimed in claim 1, it is characterized in that, described first order compressor is centrifugal compressor, and described high stage compressor is screw compressor.
3. multiple compression refrigerant-cycle systems as claimed in claim 1, it is characterized in that, described first order compressor is screw compressor, and described high stage compressor is piston compressor or scroll compressor.
4. multiple compression refrigerant-cycle systems as claimed in claim 1, it is characterized in that, described first order compressor and the first device in one-way on state are parallel to the suction side of described high stage compressor, and during to allow that described first order compressor quits work, cold-producing medium enters described high stage compressor through described first device in one-way on state.
5. multiple compression refrigerant-cycle systems as claimed in claim 1, it is characterized in that, described high stage compressor and the second device in one-way on state are parallel to the exhaust side of described first order compressor, and during to allow that described high stage compressor quits work, cold-producing medium enters the downstream of described high stage compressor after first order compressor compresses through described second device in one-way on state.
6. multiple compression refrigerant-cycle systems as claimed in claim 4, it is characterized in that, described high stage compressor and the second device in one-way on state are parallel to the exhaust side of described first order compressor, and during to allow that described high stage compressor quits work, cold-producing medium enters the downstream of described high stage compressor after first order compressor compresses through described second device in one-way on state.
7. the multiple compression refrigerant-cycle systems according to any one of claim 1 to 6, it is characterized in that, the described compression-type refrigeration agent circulatory system also comprises economizer and the second throttling arrangement, the discharge opeing side of described condenser arranges first flow path through described economizer and the second stream, enters into described first flow path and described second stream respectively to make the condensate liquid exported from described condenser; Described second throttling arrangement is provided with in described second stream, described economizer allows the mutual heat exchange of cold-producing medium of described first flow path and described second stream, with make the cold-producing medium of described first flow path through described economizer carried out cold after enter described first throttle device again, and make the cold-producing medium of described second stream by after described second throttling arrangement throttling, evaporate through described economizer again, and then enter the upstream side of described high stage compressor.
8. the multiple compression refrigerant-cycle systems according to any one of claim 1 to 6, it is characterized in that, the exhaust side of described first order compressor arranges the 3rd stream being connected to described condenser, so that described condenser receives the exhaust exceeding the described first order compressor of described high stage compressor inspiratory capacity when the capacity of described first order compressor is greater than the inspiratory capacity of described high stage compressor; The downstream of described high stage compressor is provided with water heater and the 3rd throttling arrangement, described water heater be used for hot water preparing after the exhaust condensation of described high stage compressor, described 3rd throttling arrangement be used for through described water heater cold-producing medium throttling and be discharged into described condenser; Described condenser is used for be discharged into described first throttle device after the condensation of refrigerant of reception.
9. the multiple compression refrigerant-cycle systems according to any one of claim 1 to 6, is characterized in that, the described compression-type refrigeration agent circulatory system also comprises the second evaporimeter and the 4th throttling arrangement, the exhaust side of the second compressor arranges described condenser and first throttle device, described condenser is used for the exhaust of the second compressor described in condensation, described first throttle device is used for the cold-producing medium of condenser output described in throttling and is discharged into described first evaporimeter, described first evaporimeter has two exhaust sides, one of them exhaust side is communicated with described 4th throttling arrangement, described second evaporimeter be used for by through described 4th throttling arrangement condensation of refrigerant and be discharged into the suction side of described first order compressor, another exhaust side is wherein communicated with the suction side of described high stage compressor by the 4th stream, gaseous refrigerant can be supplemented to described high stage compressor by means of described 4th stream with the second evaporimeter described in making when the capacity of described first order compressor is less than the inspiratory capacity of described high stage compressor.
10. the control method of multiple compression refrigerant-cycle systems, comprise and provide cold-producing medium at compound compressor, condenser, the closed circuit circulated successively between first throttle device and the first evaporimeter, it is characterized in that, there is provided first order compressor and high stage compressor as described compound compressor, wherein said first and described high stage compressor be the compressor with variety classes compressing mechanism, the capacity of described first order compressor is greater than the capacity of described high stage compressor, the pressure differential of described high stage compressor is greater than the pressure differential of described first order compressor, described pressure differential is the difference of pressure at expulsion and inlet pressure, described high stage compressor is connected to the exhaust side of described first order compressor,
Rated point mode of operation, medium and small load pattern, refrigeration originate mode, low-temperature heating pattern, supplying hot water pattern and/or ice-make mode are provided;
Wherein, in described rated point mode of operation, described first order compressor is utilized to carry out supercharging to cold-producing medium, recycle described high stage compressor and second compression is again carried out to described cold-producing medium, utilize condenser to the condensation of refrigerant of second compression again, divide two-way by condensed cold-producing medium, a road through economizer carried out cold after enter described first throttle device in described closed circuit, another road is evaporated through economizer, then enters described high stage compressor suction side;
At described medium and small load pattern, stop described first order compressor, only use described high stage compressor to carry out supercharging;
At described refrigeration originate mode, stop described high stage compressor, only use described first order compressor to cold-producing medium supercharging;
In described low-temperature heating pattern, on the basis of described rated point mode of operation, improve the supercharging multiple of first order compressor, high stage compressor;
In described supplying hot water pattern, the capacity of first order compressor is adjusted to the inspiratory capacity being greater than high stage compressor, first order compressor is utilized to carry out supercharging to cold-producing medium, cold-producing medium major part after supercharging is directly discharged to condenser, for refrigeration, utilize the second compressor to draw the exhaust of first order compressor remainder simultaneously, carry out second-compressed, the exhaust of the second compressor is discharged in water heater, obtain high-temperature water outlet, and carry out condensation by being discharged into described condenser after the cold-producing medium throttling of water heater further;
In described ice-make mode, the capacity of first order compressor is adjusted to the inspiratory capacity being less than high stage compressor, by the cold-producing medium after the compression of high stage compressor by condenser condenses, again by the throttling of first throttle device, cold-producing medium after throttling is evaporated by the first evaporimeter and divides two-way to export, a wherein road is turned back to the suction side of high stage compressor, will wherein after another route the 4th throttling arrangement throttling again by the second evaporator evaporation, then the suction side of first order compressor is turned back to, afterwards by the suction side being discharged to high stage compressor after first order compressor compresses, utilize cold-producing medium in the evaporation ice making of the second evaporimeter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510160812.7A CN104792051B (en) | 2015-04-07 | 2015-04-07 | Multiple compression refrigerant-cycle systems and its control method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510160812.7A CN104792051B (en) | 2015-04-07 | 2015-04-07 | Multiple compression refrigerant-cycle systems and its control method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104792051A true CN104792051A (en) | 2015-07-22 |
| CN104792051B CN104792051B (en) | 2017-11-17 |
Family
ID=53557062
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510160812.7A Active CN104792051B (en) | 2015-04-07 | 2015-04-07 | Multiple compression refrigerant-cycle systems and its control method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104792051B (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105387645A (en) * | 2015-12-17 | 2016-03-09 | 重庆美的通用制冷设备有限公司 | Water chilling unit and control method thereof |
| CN106949657A (en) * | 2017-03-10 | 2017-07-14 | 广东美的暖通设备有限公司 | Air-conditioning system and its control method with supercooling apparatus |
| JP2017190769A (en) * | 2016-04-13 | 2017-10-19 | 復盛股▲分▼有限公司 | Compression apparatus |
| CN109099607A (en) * | 2017-06-21 | 2018-12-28 | 浙江盾安人工环境股份有限公司 | Centrifugal refrigerating machines and its control method |
| CN109405366A (en) * | 2018-10-29 | 2019-03-01 | 珠海格力电器股份有限公司 | Air conditioner circulating system, the control method of air conditioner circulating system and air-conditioning |
| CN109405366B (en) * | 2018-10-29 | 2024-04-26 | 珠海格力电器股份有限公司 | Air conditioner circulation system, control method of air conditioner circulation system and air conditioner |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1430029A (en) * | 2001-12-29 | 2003-07-16 | 成都希望电子研究所 | Cold water set for air conditioner |
| US20060201171A1 (en) * | 2005-03-10 | 2006-09-14 | Sunpower, Inc. | Dual mode compressor with automatic compression ratio adjustment for adapting to multiple operating conditions |
| US20110094259A1 (en) * | 2007-10-10 | 2011-04-28 | Alexander Lifson | Multi-stage refrigerant system with different compressor types |
| CN102713463A (en) * | 2010-01-20 | 2012-10-03 | 开利公司 | Refrigeration storage in a refrigerant vapor compression system |
| CN102748900A (en) * | 2012-07-24 | 2012-10-24 | 上海伯涵热能科技有限公司 | Heat pump, heat pump air conditioner and heat pump water heating unit sequentially using single/double stage compression |
-
2015
- 2015-04-07 CN CN201510160812.7A patent/CN104792051B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1430029A (en) * | 2001-12-29 | 2003-07-16 | 成都希望电子研究所 | Cold water set for air conditioner |
| US20060201171A1 (en) * | 2005-03-10 | 2006-09-14 | Sunpower, Inc. | Dual mode compressor with automatic compression ratio adjustment for adapting to multiple operating conditions |
| US20110094259A1 (en) * | 2007-10-10 | 2011-04-28 | Alexander Lifson | Multi-stage refrigerant system with different compressor types |
| CN102713463A (en) * | 2010-01-20 | 2012-10-03 | 开利公司 | Refrigeration storage in a refrigerant vapor compression system |
| CN102748900A (en) * | 2012-07-24 | 2012-10-24 | 上海伯涵热能科技有限公司 | Heat pump, heat pump air conditioner and heat pump water heating unit sequentially using single/double stage compression |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105387645A (en) * | 2015-12-17 | 2016-03-09 | 重庆美的通用制冷设备有限公司 | Water chilling unit and control method thereof |
| JP2017190769A (en) * | 2016-04-13 | 2017-10-19 | 復盛股▲分▼有限公司 | Compression apparatus |
| CN107288883A (en) * | 2016-04-13 | 2017-10-24 | 复盛股份有限公司 | Compression apparatus |
| CN106949657A (en) * | 2017-03-10 | 2017-07-14 | 广东美的暖通设备有限公司 | Air-conditioning system and its control method with supercooling apparatus |
| CN109099607A (en) * | 2017-06-21 | 2018-12-28 | 浙江盾安人工环境股份有限公司 | Centrifugal refrigerating machines and its control method |
| CN109405366A (en) * | 2018-10-29 | 2019-03-01 | 珠海格力电器股份有限公司 | Air conditioner circulating system, the control method of air conditioner circulating system and air-conditioning |
| CN109405366B (en) * | 2018-10-29 | 2024-04-26 | 珠海格力电器股份有限公司 | Air conditioner circulation system, control method of air conditioner circulation system and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104792051B (en) | 2017-11-17 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US9612042B2 (en) | Method of operating a refrigeration system in a null cycle | |
| CN101688695B (en) | Co2 refrigerant system with booster circuit | |
| US20130180276A1 (en) | Cascade heat pump | |
| CN105737427B (en) | A kind of one-level Auto-cascade cycle low-temperature refrigeration circulating device using twin-stage gas-liquid separator | |
| CN102132112A (en) | Charge management in refrigerant vapor compression systems | |
| CN101668998A (en) | Enhanced refrigerant system | |
| US20150253040A1 (en) | Refrigerator | |
| US10101060B2 (en) | Cooling system | |
| CN105258392A (en) | Heat pump heating system, control method and heat pump water heater | |
| EP3364128B1 (en) | Heat pump unit control system | |
| US20130055754A1 (en) | Air conditioner | |
| CN104792051A (en) | Multi-stage compression refrigerant circulation system and control method thereof | |
| CN106546026A (en) | Using the non-azeotropic mixed working medium fractional condensation Duel-temperature refrigeration cycle system of ejector potentiation | |
| CN100507401C (en) | Capacity adjustable vortex compressor refrigeration system with mediate loop installed with ejector | |
| CN111707017A (en) | Low-temperature strong-heat air source heat pump system | |
| CN114111313A (en) | Dehumidification drying heat pump system fusing compressor driving type quasi loop heat pipe | |
| CN109737622B (en) | Two-stage auto-cascade low-temperature refrigeration cycle system and circulation method for enhancing efficiency of two-stage ejector | |
| JP2010078164A (en) | Refrigeration and air conditioning device | |
| US11754320B2 (en) | Refrigeration system with multiple heat absorbing heat exchangers | |
| CN108645067A (en) | A kind of Two-stage Compression cooling during rolling three-level automatic cascade refrigeration system | |
| CN109425140B (en) | Refrigeration circuit and refrigeration plant based on non-azeotropic mixed working medium | |
| CN210425610U (en) | Refrigeration system | |
| CN204787385U (en) | Air conditioner system | |
| CN111795452A (en) | Air conditioning system | |
| CN217154579U (en) | Year-round refrigeration air-cooled water chilling unit |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| EXSB | Decision made by sipo to initiate substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |