CN105674375A - Air-source multi-stage-evaporation and dual-stage-enthalpy-increase directly-heated type heating plant - Google Patents
Air-source multi-stage-evaporation and dual-stage-enthalpy-increase directly-heated type heating plant Download PDFInfo
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- CN105674375A CN105674375A CN201610196407.5A CN201610196407A CN105674375A CN 105674375 A CN105674375 A CN 105674375A CN 201610196407 A CN201610196407 A CN 201610196407A CN 105674375 A CN105674375 A CN 105674375A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D3/00—Hot-water central heating systems
- F24D3/18—Hot-water central heating systems using heat pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D19/00—Details
- F24D19/10—Arrangement or mounting of control or safety devices
- F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
- F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
- F24D19/1039—Arrangement or mounting of control or safety devices for water heating systems for central heating the system uses a heat pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
Abstract
The invention discloses an air-source multi-stage-evaporation and dual-stage-enthalpy-increase directly-heated type heating plant. The air-source multi-stage-evaporation and dual-stage-enthalpy-increase directly-heated type heating plant comprises a first-stage compressor system, a second-stage compressor system and a two-phase heat exchanger; the first-stage compressor system comprises a first-stage compressor and a first-stage evaporator; the second-stage compressor system comprises a second-stage compressor, a three-phase idle change condenser, a supercooler and a second-stage evaporator; the two-phase heat exchanger comprises a condensation channel and an evaporation channel, wherein the condensation channel is connected into the first-stage compressor system, the evaporation channel is connected into the second-stage compressor system; a water inlet and a water outlet are formed in the three-phase idle change condenser; and cold water enters the heating plant from the water inlet, and hot water flows out of the water outlet after heat exchange. The air-source multi-stage-evaporation and dual-stage-enthalpy-increase directly-heated type heating plant has the beneficial effects of being efficient, capable of saving energy, environment-friendly, safe, reliable, capable of running at low temperature and the like. No matter in rainy days or in cold winter, it can be guaranteed that high-temperature heat sources are synthesized in all weather because of the intelligent defrosting function of a heat pump unit of the air-source multi-stage-evaporation and dual-stage-enthalpy-increase directly-heated type heating plant.
Description
Technical field:
The present invention relates to heat pump product technical field, refer in particular to a kind of air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation.
Background technology:
Situations below can be there is in traditional heat pump when the use in winter that temperature is relatively low:
1. outside air temperature can reduce the cold-producing medium caloric receptivity to outdoor air when declining in the winter time. As shown in Figure 1, unit mass refrigerating capacity Q0 1=h1-h4, when outdoor temperature reduces, evaporating temperature will be dropped to t02 by t01 therewith, and unit mass refrigerating capacity is also reduced to Q02 by Q01, Q02=h1`-h4`. The reduction of unit mass refrigerating capacity means: the minimizing of the heat Q0 absorbed in cold-producing medium air outdoor. And air source heat pump is to the heating load QK=Q0+W (merit) in room, owing to the reduction of Q0 can directly contribute the decline of QK, cause heat pump undercapacity.
2. the decline of outside air temperature in winter can make compressor efficiency decline. it is mentioned above when winter, outside air temperature declined, evaporating temperature t0 and evaporating pressure P0 is also with reduction, condensing pressure PK is then by medium (room air, water) restriction and change little, so necessarily cause that pressure ratio PK/P0 increases, the increase of pressure ratio can make compressor irreversibility in the course of the work strengthen, efficiency reduces, as (PK/P0) > 20 time, conventional piston compressor is little to air-breathing (Vehicles Collected from Market is used mostly vortex or screw compressor), so, compressor decline of work efficiency when outdoor low temperature is also one of reason of air-cooled heat pump undercapacity.
3. the decline of outside air temperature in winter can cause the frosting of evaporator surface, and when winter, outside air temperature was gradually reduced, the temperature of evaporator plate tube-surface will decrease. When lower than air dew point temperature, air can condense in coil surface, and the heat exchange that now coil surface occurs will become phase-change heat-exchange, and this point is beneficial to improve the heating capacity of source pump; But when temperature continues to decline, coil surface temperature lower than air freezing point temperature (less than 0 DEG C), and if now qualified words of the relative humidity of air, coil pipe face will frosting.Such as defrost not in time, frost layer will be tied thicker and thicker, considerably increases the flow resistance of air, increases the thermal resistance of dish simultaneously, has had a strong impact on the heat transfer effect of cold-producing medium and outdoor air. So that heat pump undercapacity. More seriously, sometimes also freezing at evaporator plate tube-surface, be made evaporating pressure drop too low owing to refrigerant liquid can not well evaporate, compressor is it is possible that the shutdown of low-voltage variation.
Owing to winter temperature reduction can make the compression ratio of compressor increase, and then reduce the work efficiency of compressor, when required heat supply temperature is more high, its condensation temperature improves, condensing pressure also increases compression ratio and increases further, and Energy Efficiency Ratio sharply declines and causes that air source heat pump undercapacity in winter heating capacity significantly reduces.
Current heat pump in the winter time time, although the at present conventional Defrost mode of defrosting is a lot, such as electric defrosting, liquid defrosting and hot gas defrosting. Wherein hot gas defrosting adopt four-way change-over valve commutation defrosting more. Actually, the control for defrosting is of paramount importance. But defrosting control system according to what signal judges to carry out defrosting maybe to stop defrosting, and this problem is always up what all multi-experts in home and abroad were studied actually.
Air-cooled heat pump undercapacity in the winter time, often appears as wind pushing temperature or leaving water temperature lower than design load, generally all adopts before air-supply outlet or installs auxiliary heater additional on supply channel, to improve air-supply and the temperature supplied water. But the auxiliary heater used is usually electric heater, if use by day with unit simultaneously, substantial amounts of electric energy will necessarily be consumed in peak times of power consumption, and electricity price expensive during peak of power consumption can bring huge operating cost to user.
By the restriction of conventional refrigerant performance and operating pressure, even if reducing Energy Efficiency Ratio, it is also difficult to obtain the hot water higher than 55 DEG C, the technology path studying special cold-producing medium is mostly continued to use in the trial of heat pump high temperature application.
Summary of the invention:
The present invention asks for and solves the technical problem that and be that and overcome the deficiencies in the prior art, it is provided that a kind of air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation.
In order to solve above-mentioned technical problem, present invention employs following technical proposals: this air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation includes: stage compressor system, split-compressor system and simultaneously with the biphase heat exchanger of one-level, split-compressor system connectivity, described stage compressor system includes: stage compressor, one-level vaporizer; Described split-compressor system includes: the lazy condenser that turns cold of split-compressor, three-phase, subcooler and secondary evaporimeter; Described biphase heat exchanger includes condensation channel and evaporation channel, and wherein condensation channel is connected in stage compressor system; Described evaporation channel is connected in split-compressor system; Arranging water inlet and outlet on the lazy condenser that turns cold of described three-phase, cold water is entered by water inlet, after heat exchange, outlet flows out hot water.
Furthermore, in technique scheme, in described stage compressor system, cold-producing medium enters the condensation channel of biphase heat exchanger after stage compressor compresses, after being absorbed heat by the one-level choke valve finned one-level vaporizer of entrance after cold-producing medium condensation, it is again introduced in stage compressor and is circulated compression.
Furthermore, in technique scheme, in described stage compressor system, between the outlet of biphase heat exchanger condensation channel and one-level choke valve, it is provided with coolant ball valve, device for drying and filtering and liquid-sighting glass; It is provided with gas-liquid separator between one-level vaporizer and stage compressor.
Furthermore, in technique scheme, in described stage compressor system, between stage compressor and one-level vaporizer, it is provided with defrosting channel, on this defrosting channel, is provided with electromagnetic valve.
Furthermore, in technique scheme, in described split-compressor system, cold-producing medium enters the lazy condenser that turns cold of shell-tube type three-phase after split-compressor compresses and carries out heat release, and the cold water entered by water inlet is heated, water or steam after heating are discharged by the outlet of the lazy condenser that turns cold of three-phase; Cold-producing medium enters subcooler after the lazy condenser that turns cold of three-phase, after subcooler is supercool, enter the heat absorption of finned secondary evaporimeter by two-step throttle valve carry out cold-producing medium sensible heat increasing enthalpy, subsequently into subcooler, cold-producing medium sensible heat is carried out one-level and increase enthalpy, then pass through the evaporation channel of biphase heat exchanger, carry out two grades and increase enthalpy, increasing the degree of superheat of cold-producing medium, last cold-producing medium is again introduced in split-compressor to be circulated compression.
Furthermore, in technique scheme, in described split-compressor system, being provided with intake tunnel on the water inlet of the described lazy condenser that turns cold of three-phase and between external source, this intake tunnel is through the oil cooler of split-compressor.
Furthermore, in technique scheme, described intake tunnel is provided with check valve.
Furthermore, in technique scheme, in described split-compressor system, between subcooler condensate outlet and two grades of level choke valves, it is provided with coolant ball valve, device for drying and filtering and liquid-sighting glass.
Furthermore, in technique scheme, in described split-compressor system, between split-compressor and secondary evaporimeter, it is provided with defrosting channel, on this defrosting channel, is provided with electromagnetic valve.
Furthermore, in technique scheme, described one-level vaporizer and secondary evaporimeter all adopt the mode that at least two vaporizer is in parallel.
The technology of the present invention is based on a kind of energy-saving and environmental protection set up against Carnot cycle principle and heats heat pump techniques, is a kind of heating equipment that can substitute boiler. Air source heat-obtaining heating technology is at present state-of-the-art in the world to heat one of technology, with cold-producing medium for medium, cold-producing medium absorbs the tow taste heat in air in finned evaporator, after heating then through compressor compresses, water is transferred heat to by heat-exchanger rig, carrying out hot water preparing, hot water is sent into user's radiator by water circulation system and is carried out heating, and whole system collecting efficiency is high.
The present invention has the advantages that compared with prior art
1, energy-efficient: the present invention runs heating using air as energy sources, affected by environment little, collecting efficiency is high, the system design of optimization, operates steadily, and cost is low, and power consumption is 1/4th of electric heater compared with other like products;
2, environmental protection: the present invention runs without any comburant and emission, and cold-producing medium is to ozone layer no pollution. Air can be a kind of low-grade energy being widely present, can freely utilizing, and utilizes this system circulating technology to improve its energy grad;
3, safe and reliable: the present invention runs without the danger such as inflammable, explosive, poisoning, short-circuit that may be present in conventional boiler fuel oil, combustion gas, electric boiler, is a kind of safe and reliable air heat energy high temperature heating.
4, cold operation: no matter be overcast and rainy or Cold Winter, the intelligent defrosting function of the source pump of the present invention, it is ensured that round-the-clock synthesizing high temperature thermal source.
Accompanying drawing illustrates:
Fig. 1 is the pressure-enthalpy chart of heat pump in prior art;
Fig. 2 is the pressure-enthalpy chart of the present invention;
Fig. 3 is the structure principle chart of the present invention;
Fig. 4 is the structural representation of the present invention.
Detailed description of the invention:
Below in conjunction with specific embodiments and the drawings, the present invention is further described.
As shown in Figure 2: the present invention is a kind of cold-producing medium heat exchange condensers of slow cooling and sluggish phase change in condenser that can make, the condensation time making heat pump condenser is elongated, the warm-up heating period of water is elongated, make full use of refrigerant high pressure end superheated steam water temperature is promoted, make leaving water temperature be significantly larger than condensation temperature. The heat exchange principle of conventional heat pump condenser makes leaving condenser water temperature lower than condensation temperature.
As shown in Figure 3, this is the structure principle chart of the present invention, comprising: stage compressor system 10, split-compressor system 20 and the biphase heat exchanger 3 that simultaneously connects with one-level, split-compressor system 10,20. Described stage compressor system 10 includes: stage compressor 1, one-level vaporizer 4; Described split-compressor system 20 includes: the lazy condenser 5 that turns cold of split-compressor 2, three-phase, subcooler 6 and secondary evaporimeter 7; Described biphase heat exchanger 3 includes condensation channel and evaporation channel, and wherein condensation channel is connected in stage compressor system 10; Described evaporation channel is connected in split-compressor system 20; Arranging water inlet 51 and outlet 52 on the lazy condenser 5 that turns cold of described three-phase, cold water is entered by water inlet 51, after heat exchange, outlet 52 flows out hot water or steam.
In described stage compressor system 10, cold-producing medium enters the condensation channel of biphase heat exchanger 3 after stage compressor 1 compresses, enter after finned one-level vaporizer 4 absorbs heat by one-level choke valve 11 after cold-producing medium condensation, be again introduced in stage compressor 1 and be circulated compression.
In described split-compressor system 20, cold-producing medium enters the lazy condenser 5 that turns cold of shell-tube type three-phase after split-compressor 2 compresses and carries out heat release, and the cold water entered by water inlet 51 is heated, water or steam after heating are discharged by the outlet 52 of the lazy condenser 5 that turns cold of three-phase; Cold-producing medium enters subcooler 6 after the lazy condenser 5 that turns cold of three-phase, after subcooler 6 is supercool by two-step throttle valve 21 enter finned secondary evaporimeter 7 absorb heat cold-producing medium sensible heat is carried out increase enthalpy, subsequently into subcooler 6, cold-producing medium sensible heat is carried out one-level and increase enthalpy, then pass through the evaporation channel of biphase heat exchanger 3, carry out two grades and increase enthalpy, increasing the degree of superheat of cold-producing medium, last cold-producing medium is again introduced in split-compressor 2 and is circulated compression.
The operation principle of the present invention is: stage compressor 1 compresses cold-producing medium and carries out isentropic Compression lifting system. Refrigerant pressure and temperature enter biphase heat exchanger 3 and carry out exothermic condensation, biphase heat exchanger 3 belongs to stage compressor system 10 and split-compressor system 20 composite device, biphase heat exchanger 3 is divided into two passages, condensation channel and evaporation channel, stage compressor system 10 uses condensation channel, split-compressor system 20 to use evaporation channel.
During work, stage compressor system 10 condensation temperature, pressure are relatively low, its Main Function be, system compresses low in environmental working condition temperature as split-compressor system 20 than big, heat efficiency low as heat-obtaining thermal source, ensure that stage compressor system 10 possesses normal system compresses ratio under extremely low ambient temperature simultaneously. In biphase heat exchanger 3, condensed cold-producing medium enters finned one-level vaporizer 4 through the one-level choke valve 11 (employing electric expansion valve) of stage compressor system 10 and is evaporated, utilize evaporation latent heat to absorb the low-grade heat source in natural environment simultaneously, forming saturated vapor or superheated steam after making cold-producing medium heat absorption, then cold-producing medium saturated vapor or superheated vapor enter stage compressor 1 and are circulated reciprocating compression.
During work, compress cold-producing medium by split-compressor 2 and carry out isentropic Compression, after promoting refrigerant pressure and temperature, cold-producing medium enters the lazy condenser 5 that turns cold of shell-tube type three-phase and carries out exothermic condensation output high-temperature-hot-water, after condensation, cold-producing medium is then through subcooler 6, to secondary evaporimeter 7 return-air in split-compressor system 20, after utilizing condensation, liquid refrigerant sensible heat carries out increasing enthalpy, increase the degree of superheat of secondary evaporimeter 7 inner refrigerant in split-compressor system 20, increase the lazy condenser 5 that turns cold of three-phase simultaneously and export the degree of supercooling of cold-producing medium. Supercool rear cold-producing medium enters fin two-stage type vaporizer through split-compressor system 20 two-step throttle valve 21 (employing electric expansion valve) and is evaporated. Utilizing evaporation latent heat to absorb the low-grade heat source in natural environment, after evaporation, cold-producing medium is after subcooler 6 condenses, and liquid refrigerant sensible heat carries out increasing enthalpy, increases enthalpy then through biphase heat exchanger 3 and increases the degree of superheat. When split-compressor system 20 suction temperature is higher than setting value, stage compressor system 10 does not start, and biphase heat exchanger 3 is only used as pipeline and passes through.
The heat order that split-compressor system 20 evaporation absorbs is followed successively by: the condensation heat of natural environment middle-low grade thermal source, three-phase lazy turn cold condenser 5 waste heat of condensation, stage compressor system 10.
Stage compressor system 10 condensation heat relative temperature is higher, wherein comprises the discharge superheat vapor (steam) temperature of the stage compressor 1 of higher temperature, but heats total amount and account for small percentage in total system. primarily serve the purpose of and under low temperature environment, split-compressor system 20 is carried out auxiliary increasing enthalpy, make split-compressor system 20 under low temperature ambient conditions, evaporation operating mode ambient temperature uprises, promote evaporation suction temperature and improve evaporating pressure, increase inspiration capacity, split-compressor system 20 is made to obtain higher delivery temperature and more heat under relatively low pressure at expulsion, make split-compressor system 20 can evaporate heat-obtaining when ambient temperature is extremely low simultaneously, and possess normal system compresses ratio, the lazy condenser 5 that turns cold of split-compressor system 20 shell-tube type three-phase is utilized can stably to input high temperature heat source under extremely low temperature ambient temperature to user side.
Shown in Fig. 4, this is the structure chart of specific embodiment of the invention. Shown in Fig. 3, in concrete structure figure of the present invention, in described stage compressor system 10, between the outlet of biphase heat exchanger 3 condensation channel and one-level choke valve 11, it is provided with coolant ball valve RU1, device for drying and filtering FG1 and liquid-sighting glass IPL1; Gas-liquid separator GLS it is provided with between one-level vaporizer 4 and stage compressor 1. Meanwhile, between stage compressor 1 and one-level vaporizer 4, it is provided with defrosting channel 12, on this defrosting channel 12, is provided with electromagnetic valve YV1.
Same, in the concrete structure of the present invention, in described split-compressor system 20, being provided with intake tunnel 511 on the water inlet 51 of the described lazy condenser 5 that turns cold of three-phase and between external source, this intake tunnel 511 is through the oil cooler 22 of split-compressor 2. Described intake tunnel 511 is provided with check valve HV. Same, in described split-compressor system, between subcooler 6 condensate outlet and two grades of level choke valves 21, it is provided with coolant ball valve RU2, device for drying and filtering FG2 and liquid-sighting glass IPL2.
In split-compressor system, between split-compressor 2 and secondary evaporimeter 7, it is provided with defrosting channel 23, on this defrosting channel 23, is provided with electromagnetic valve YV2.
In order to increase the evaporation capacity of vaporizer, in concrete structure of the present invention, one-level vaporizer 4 and secondary evaporimeter 7 all adopt the mode that two vaporizers are in parallel. , it is possible to adopt one, or plural parallel way certainly.
The specific works process of the present invention is: stage compressor 1 compresses cold-producing medium and carries out isentropic Compression, promotes system refrigerant pressure and temperature enters biphase heat exchanger 2 and carries out exothermic condensation. In biphase heat exchanger 2, after condensation, cold-producing medium, after the coolant ball valve RU1 of stage compressor system 10, device for drying and filtering FG1, liquid-sighting glass IPL1, electric expansion valve ETC1 (i.e. one-level choke valve 11), enters finned one-level vaporizer 4 and is evaporated. Utilize evaporation latent heat to absorb the low-grade heat source in natural environment air simultaneously, saturated vapor or superheated steam is formed after making cold-producing medium heat absorption, cold-producing medium saturated vapor or superheated vapor enter gas-liquid separator GLS, entered stage compressor 1 by gas-liquid separator GLS again and be circulated reciprocating compression, when in stage compressor system 10, vaporizer 4 surface temperature and ambient temperature differences are more than defrost temperature difference, electromagnetic valve YV1 opens and carries out increasing enthalpy defrosting.
Split-compressor 2 compresses cold-producing medium and carries out isentropic Compression, after promoting system refrigerant pressure and temperature, cold-producing medium enters the lazy condenser 5 that turns cold of shell-tube type three-phase and carries out exothermic condensation output high-temperature-hot-water, after condensation, cold-producing medium sensible heat of cold-producing medium saturated liquid after subcooler 6 discharges condensation increases enthalpy for secondary evaporimeter 7 return-air, increases the lazy condenser 5 that turns cold of three-phase in split-compressor system 2 simultaneously and exports cold-producing medium degree of supercooling. Cold-producing medium enters secondary evaporimeter 7 absorb natural air middle-low grade thermal source through coolant ball valve RU2, device for drying and filtering FG2, liquid-sighting glass IPL2, electric expansion valve ETC2, be again introduced into subcooler 6 carry out increase enthalpy increase the degree of superheat, enter biphase heat exchanger 3 carry out increase enthalpy increase the degree of superheat, enter back into split-compressor 2 and be circulated reciprocating compression.
The condensation heat that heat is split-compressor system 20 that secondary evaporimeter 7 return-air absorbs under extremely low temperature ambient temperature, the discharge superheat vapor (steam) temperature of the higher stage compressor 1 wherein comprising higher temperature of condensation heat relative temperature, make split-compressor system 20 evaporitic environment working temperature height, evaporating temperature is high, make split-compressor system 20 obtain higher delivery temperature under relatively low ambient temperature and pressure at expulsion, makes split-compressor system 20 possess normal system compresses ratio when ambient temperature is extremely low simultaneously. When secondary evaporimeter 7 surface temperature and the ambient temperature differences of split-compressor system 20 is more than defrost temperature difference, cold-producing medium electromagnetic valve YV2 opens and carries out increasing enthalpy defrosting.
Certainly, the foregoing is only specific embodiments of the invention, not being limit the scope of the present invention, all equivalences done according to structure, feature and principle described in the present patent application the scope of the claims change or modify, and all should be included in the present patent application the scope of the claims.
Claims (10)
1. air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation, comprising: stage compressor system (10), split-compressor system (20) and the biphase heat exchanger (3) that simultaneously connects with one-level, split-compressor system (10,20), it is characterised in that:
Described stage compressor system (10) including: stage compressor (1), one-level vaporizer (4);
Described split-compressor system (20) including: the lazy condenser that turns cold (5) of split-compressor (2), three-phase, subcooler (6) and secondary evaporimeter (7);
Described biphase heat exchanger (3) includes condensation channel and evaporation channel, and wherein condensation channel is connected in stage compressor system (10); Described evaporation channel is connected in split-compressor system (20);
Arranging water inlet and outlet on the lazy condenser that turns cold (5) of described three-phase, cold water is entered by water inlet, after heat exchange, outlet flows out hot water.
2. air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation according to claim 1, it is characterized in that: in described stage compressor system, cold-producing medium enters the condensation channel of biphase heat exchanger (3) after stage compressor (1) compresses, enter after finned one-level vaporizer (4) absorbs heat by one-level choke valve (11) after cold-producing medium condensation, be again introduced in stage compressor (1) and be circulated compression.
3. air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation according to claim 2, it is characterized in that: in described stage compressor system, between the outlet of biphase heat exchanger (3) condensation channel and one-level choke valve (11), be provided with coolant ball valve (RU1), device for drying and filtering (FG1) and liquid-sighting glass (IPL1); Gas-liquid separator (GLS) it is provided with between one-level vaporizer (4) and stage compressor (1).
4. air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation according to claim 3, it is characterized in that: in described stage compressor system, between stage compressor (1) and one-level vaporizer (4), it is provided with defrosting channel (12), on this defrosting channel (12), is provided with electromagnetic valve (YV1).
5. the air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation according to any one in claim 1-4, it is characterized in that: in described split-compressor system, cold-producing medium enters the lazy condenser that turns cold (5) of shell-tube type three-phase after split-compressor (2) compresses and carries out heat release, and the cold water entered by water inlet (51) is heated, water or steam after heating are discharged by the outlet (52) of the lazy condenser that turns cold (5) of three-phase; Cold-producing medium enters subcooler (6) after the lazy condenser that turns cold (5) of three-phase, after subcooler (6) is supercool, enter finned secondary evaporimeter (7) heat absorption by two-step throttle valve (21) carry out cold-producing medium sensible heat increasing enthalpy, subsequently into subcooler (6), cold-producing medium sensible heat is carried out one-level and increase enthalpy, then pass through the evaporation channel of biphase heat exchanger (3), carry out two grades and increase enthalpy, increasing the degree of superheat of cold-producing medium, last cold-producing medium is again introduced in split-compressor (2) and is circulated compression.
6. air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation according to claim 5, it is characterized in that: in described split-compressor system, water inlet (51) in the described lazy condenser that turns cold (5) of three-phase above and is provided with intake tunnel (511) between external source, and this intake tunnel (511) is through the oil cooler (22) of split-compressor (2).
7. air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation according to claim 6, it is characterised in that: described intake tunnel (511) is provided with check valve (HV).
8. air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation according to claim 5, it is characterized in that: in described split-compressor system, between subcooler (6) condensate outlet and two grades of level choke valves (21), be provided with coolant ball valve (RU2), device for drying and filtering (FG2) and liquid-sighting glass (IPL2).
9. air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation according to claim 2, it is characterized in that: in described split-compressor system, between split-compressor (2) and secondary evaporimeter (7), it is provided with defrosting channel (23), on this defrosting channel (23), is provided with electromagnetic valve (YV2).
10. air source multistage evaporation two-stage enthalpy increasing directly-heated type heating installation according to claim 1, it is characterised in that: described one-level vaporizer (4) and secondary evaporimeter (7) all adopt the mode that at least two vaporizer is in parallel.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106440459A (en) * | 2016-10-26 | 2017-02-22 | 广东高而美制冷设备有限公司 | Auxiliary heating enthalpy-increasing heat pump system and working mode thereof |
| CN107606811A (en) * | 2017-09-27 | 2018-01-19 | 南京师范大学 | A kind of cryogenic refrigeration systems and its operation method |
| CN115264977A (en) * | 2022-07-29 | 2022-11-01 | 哈尔滨工业大学 | High-temperature water working medium heat pump circulating system with intermediate multi-stage cooling in compression process |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1436980A (en) * | 2003-02-28 | 2003-08-20 | 浙江大学 | Method and mechanism for expanding heat producing capacity of heat pump under low temperature environment |
| CN101275792A (en) * | 2008-05-19 | 2008-10-01 | 南京理工大学 | Single / double stage mixed composite stacking heat pump air conditioner unit |
| CN101957061A (en) * | 2010-11-03 | 2011-01-26 | 湖南利能科技股份有限公司 | Quasi-two-stage compression ultralow temperature air source heat pump water heater with economizer |
| CN202382481U (en) * | 2011-11-24 | 2012-08-15 | 上海环球制冷设备有限公司 | Super-high temperature heat pump device |
| JP2012202678A (en) * | 2011-03-28 | 2012-10-22 | Mitsubishi Electric Corp | Refrigerating cycle apparatus |
| CN202675719U (en) * | 2012-06-07 | 2013-01-16 | 四川同达博尔置业有限公司 | Air-cooled heat pump air conditioner |
| CN205536061U (en) * | 2016-03-31 | 2016-08-31 | 广东衡峰热泵设备科技有限公司 | Multistage evaporation doublestage in air source increases enthalpy directly -heated type heating system |
-
2016
- 2016-03-31 CN CN201610196407.5A patent/CN105674375A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1436980A (en) * | 2003-02-28 | 2003-08-20 | 浙江大学 | Method and mechanism for expanding heat producing capacity of heat pump under low temperature environment |
| CN101275792A (en) * | 2008-05-19 | 2008-10-01 | 南京理工大学 | Single / double stage mixed composite stacking heat pump air conditioner unit |
| CN101957061A (en) * | 2010-11-03 | 2011-01-26 | 湖南利能科技股份有限公司 | Quasi-two-stage compression ultralow temperature air source heat pump water heater with economizer |
| JP2012202678A (en) * | 2011-03-28 | 2012-10-22 | Mitsubishi Electric Corp | Refrigerating cycle apparatus |
| CN202382481U (en) * | 2011-11-24 | 2012-08-15 | 上海环球制冷设备有限公司 | Super-high temperature heat pump device |
| CN202675719U (en) * | 2012-06-07 | 2013-01-16 | 四川同达博尔置业有限公司 | Air-cooled heat pump air conditioner |
| CN205536061U (en) * | 2016-03-31 | 2016-08-31 | 广东衡峰热泵设备科技有限公司 | Multistage evaporation doublestage in air source increases enthalpy directly -heated type heating system |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106440459A (en) * | 2016-10-26 | 2017-02-22 | 广东高而美制冷设备有限公司 | Auxiliary heating enthalpy-increasing heat pump system and working mode thereof |
| CN107606811A (en) * | 2017-09-27 | 2018-01-19 | 南京师范大学 | A kind of cryogenic refrigeration systems and its operation method |
| CN115264977A (en) * | 2022-07-29 | 2022-11-01 | 哈尔滨工业大学 | High-temperature water working medium heat pump circulating system with intermediate multi-stage cooling in compression process |
| CN115264977B (en) * | 2022-07-29 | 2024-03-29 | 哈尔滨工业大学 | Intermediate multistage cooling high-temperature water working medium heat pump circulating system in compression process |
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