CN108844253B - Super-high temperature non-azeotropic working medium heat pump unit - Google Patents
Super-high temperature non-azeotropic working medium heat pump unit Download PDFInfo
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- CN108844253B CN108844253B CN201811036483.5A CN201811036483A CN108844253B CN 108844253 B CN108844253 B CN 108844253B CN 201811036483 A CN201811036483 A CN 201811036483A CN 108844253 B CN108844253 B CN 108844253B
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- 239000003507 refrigerant Substances 0.000 claims abstract description 126
- 238000011069 regeneration method Methods 0.000 claims abstract description 46
- 238000000034 method Methods 0.000 claims abstract description 35
- 230000008569 process Effects 0.000 claims abstract description 34
- 230000008929 regeneration Effects 0.000 claims abstract description 25
- 238000009833 condensation Methods 0.000 claims abstract description 23
- 230000005494 condensation Effects 0.000 claims abstract description 23
- 238000001704 evaporation Methods 0.000 claims abstract description 20
- 238000010521 absorption reaction Methods 0.000 claims abstract description 19
- 230000008020 evaporation Effects 0.000 claims abstract description 19
- 239000002918 waste heat Substances 0.000 claims abstract description 16
- 239000002440 industrial waste Substances 0.000 claims abstract description 7
- 238000010438 heat treatment Methods 0.000 claims abstract description 4
- 239000007788 liquid Substances 0.000 claims description 84
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 43
- 239000006096 absorbing agent Substances 0.000 claims description 29
- 239000002826 coolant Substances 0.000 claims description 10
- 230000005484 gravity Effects 0.000 claims description 9
- MSSNHSVIGIHOJA-UHFFFAOYSA-N pentafluoropropane Chemical compound FC(F)CC(F)(F)F MSSNHSVIGIHOJA-UHFFFAOYSA-N 0.000 claims description 8
- 230000002745 absorbent Effects 0.000 claims description 7
- 239000002250 absorbent Substances 0.000 claims description 7
- 239000000203 mixture Substances 0.000 claims description 6
- 230000009471 action Effects 0.000 claims description 4
- 230000009467 reduction Effects 0.000 claims description 4
- 239000007789 gas Substances 0.000 claims description 3
- 239000007791 liquid phase Substances 0.000 claims description 3
- 239000012071 phase Substances 0.000 claims description 3
- 238000005516 engineering process Methods 0.000 abstract description 8
- 239000000243 solution Substances 0.000 description 86
- AMXOYNBUYSYVKV-UHFFFAOYSA-M lithium bromide Chemical compound [Li+].[Br-] AMXOYNBUYSYVKV-UHFFFAOYSA-M 0.000 description 26
- 239000000126 substance Substances 0.000 description 4
- YFMFNYKEUDLDTL-UHFFFAOYSA-N 1,1,1,2,3,3,3-heptafluoropropane Chemical compound FC(F)(F)C(F)C(F)(F)F YFMFNYKEUDLDTL-UHFFFAOYSA-N 0.000 description 2
- 150000001298 alcohols Chemical class 0.000 description 2
- 230000002427 irreversible effect Effects 0.000 description 2
- IPLONMMJNGTUAI-UHFFFAOYSA-M lithium;bromide;hydrate Chemical compound [Li+].O.[Br-] IPLONMMJNGTUAI-UHFFFAOYSA-M 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 150000003839 salts Chemical class 0.000 description 2
- NKTUMKCOWFYOLC-UHFFFAOYSA-M OCC(F)(F)F.[Li+].[Br-] Chemical compound OCC(F)(F)F.[Li+].[Br-] NKTUMKCOWFYOLC-UHFFFAOYSA-M 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- VXJIMUZIBHBWBV-UHFFFAOYSA-M lithium;chloride;hydrate Chemical compound [Li+].O.[Cl-] VXJIMUZIBHBWBV-UHFFFAOYSA-M 0.000 description 1
- WAZWGFFJLSIDMX-UHFFFAOYSA-M lithium;iodide;hydrate Chemical compound [Li+].O.[I-] WAZWGFFJLSIDMX-UHFFFAOYSA-M 0.000 description 1
- IADULSDNXCPSMU-UHFFFAOYSA-M lithium;methanol;bromide Chemical compound [Li+].[Br-].OC IADULSDNXCPSMU-UHFFFAOYSA-M 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 239000002480 mineral oil Substances 0.000 description 1
- 235000010446 mineral oil Nutrition 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 229910052755 nonmetal Inorganic materials 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000012266 salt solution Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- -1 trifluoro dichloroethane-dimethanol tetraethylene glycol Chemical compound 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/02—Compression-sorption 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Sorption Type Refrigeration Machines (AREA)
Abstract
The invention provides an ultra-high temperature non-azeotropic heat pump unit, which combines a condenser of an electric heat pump and an evaporator regenerator of an absorption heat pump into a whole, and simultaneously realizes the processes of Freon condensation, solution regeneration and refrigerant evaporation. Meanwhile, a novel non-azeotropic working medium HD-01 is used in the electric heat pump, and the condensing temperature of the novel non-azeotropic working medium can reach more than 130 ℃. The ultra-high temperature non-azeotropic heat pump unit can be used for recovering industrial waste heat below 50 ℃ and heating a heated medium to above 180 ℃. Compared with the current electric heat pump technology or absorption heat pump technology, the method can realize higher outlet temperature and temperature rise of the heated medium at the same waste heat resource temperature, and has certain economic advantages.
Description
Technical Field
The invention belongs to the technical field of energy utilization, and particularly relates to an ultra-high temperature heat pump adopting non-azeotropic working media.
Background
In the fields of energy chemical industry and the like, a large amount of low-grade waste heat exists widely, and the waste heat is directly discharged in a low-temperature water or steam mode and is not utilized, so that the energy utilization efficiency of the system is low due to the large amount of the waste heat.
The existing industrial waste heat recovery technology is a heat pump technology, if an absorption heat pump technology is adopted, whether the absorption heat pump technology is a type of absorption heat pump or a type of absorption heat pump, the outlet temperature of a heated medium is limited due to the flow of the absorption heat pump or the limitation of lithium bromide working medium; if the electric heat pump technology is adopted, the temperature rising range is very limited due to the limitation of a compressor and working media when the electric heat pump adopts pure working media, and the economical efficiency is poor due to higher electricity consumption.
The existing absorption heat pump and electric heat pump are used in a mode of connecting external waterways in series or in parallel, and because each heat exchanger of the heat pump has a heat exchange end difference, irreversible loss is caused in the heat exchange process, and the performance of the system is poor.
In order to realize the great increase of the temperature of the heated medium, the invention provides a novel heat exchange device which integrates an electric heat pump condenser and an absorption heat pump regenerator evaporator, can recover industrial waste heat below 50 ℃ and can simultaneously increase the temperature of the heated medium to more than 180 ℃; compared with the prior reported heat pump technology, the heat pump adopting the novel flow and the heat exchange device has the characteristics of higher outlet temperature and larger temperature rise amplitude.
Disclosure of Invention
In order to solve the problem that the temperature difference between the waste heat resource and the temperature of the heated medium is too large and difficult to recover in the waste heat recovery process, the invention provides a heat pump unit which combines a non-azeotropic working medium electric heat pump and an absorption heat pump, the heat pump unit does not simply connect a water path of the electric heat pump and a water path of the absorption heat pump in series or in parallel, and the like, but combines a condenser of the electric heat pump and an evaporator regenerator of the absorption heat pump into a whole, compared with the prior art, the invention reduces the irreversible loss in the heat exchange process due to the innovation of the process, and simultaneously uses a novel non-azeotropic working medium in the electric heat pump, thereby having higher heat pump COP (coefficient of performance), and the heat pump can recover industrial waste heat below 50 ℃ and heat the heated medium to above 180 ℃.
The invention combines the condenser, the absorption heat pump regenerator and the absorption heat pump evaporator of the electric heat pump into one, and the novel three-in-one heat exchanger simultaneously realizes the processes of non-azeotropic working medium condensation in the inner heat exchange tube, solution regeneration outside the tube and refrigerant water evaporation.
The invention provides an ultra-high temperature non-azeotropic working medium heat pump unit which comprises an evaporator 1, a condenser 4, a condensation-evaporation-regeneration heat exchanger 3, an absorber 5, an electric compressor 2, a circulating pump throttle valve and other accessories.
The evaporator 1 of the heat pump unit is communicated with the condensing-evaporating-regenerating heat exchanger 3 through a pipeline, the condenser 4 is communicated with the condensing-evaporating-regenerating heat exchanger 3 through a pipeline, and the absorber 5 is communicated with the condensing-evaporating-regenerating heat exchanger 3 through a pipeline.
The connecting pipeline of the evaporator 1 of the heat pump comprises a waste heat water pipeline 15, a non-azeotropic working medium (liquid state) pipeline 16 and a non-azeotropic working medium (vapor state) pipeline 20; the liquid zeotropic working medium is vaporized from liquid state to vapor state after entering the evaporator 1 through the zeotropic working medium (liquid) pipeline 16 and being heated by the industrial waste heat medium in the waste heat water pipeline 15, and then the vapor state zeotropic working medium enters the zeotropic working medium (vapor state) pipeline 20 and leaves the evaporator 1 and then enters the electric compressor 2.
The connecting pipelines of the absorber 5 of the heat pump comprise a refrigerant (steam state) pipeline 21, a dilute solution pipeline 24, a concentrated solution pipeline 22 and a heated medium pipeline 23; the concentrated solution is fed into the absorber 5 to absorb the refrigerant vapor from the refrigerant (vapor state) line 21 during the flow, and the concentration of the solution is reduced during the absorption while releasing heat for heating the medium in the heated medium line 23; the lean solution that finally completes the absorption process leaves the absorber 5 through the lean solution line 24.
The connecting lines of the condenser 4 of the heat pump comprise a refrigerant (vapour) line 19, a refrigerant (liquid) line 17 and a cooling medium line 18; the refrigerant vapor enters the condenser 4 through a refrigerant (vapor state) pipeline 19 and then exchanges heat with a cooling medium pipeline 18 to be cooled, so that the refrigerant vapor is changed into a liquid state from the vapor state, and the liquid-state refrigerant enters a refrigerant (liquid state) pipeline 17 and leaves the condenser 4.
The condensation-evaporation-regeneration heat exchanger 3 of the heat pump comprises a non-azeotropic working medium condensation cavity 8, a refrigerant evaporation cavity 6 and a solution regeneration cavity 7; the connecting pipelines of the condensation-evaporation-regeneration heat exchanger 3 comprise a non-azeotropic working medium (vapor state) pipeline 20, a refrigerant (liquid state) pipeline 17, a refrigerant (vapor state) pipeline 21, a non-azeotropic working medium (liquid state) pipeline 16, a dilute solution pipeline 24, a concentrated solution pipeline 22 and a refrigerant (vapor state) pipeline 19; the condensation-evaporation-regeneration heat exchanger 3 simultaneously realizes the heat exchange process of non-azeotropic working medium condensation, dilute solution regeneration and liquid refrigerant evaporation; the non-azeotropic working medium condensation cavity 8 inside the condensation-evaporation-regeneration heat exchanger 3 realizes the condensation process that the vapor non-azeotropic working medium from the non-azeotropic working medium (vapor) pipeline 20 changes from gas phase to liquid phase in the space in the heat transfer pipe 9, and the liquid non-azeotropic working medium formed by condensation enters the non-azeotropic working medium (liquid) pipeline 16; the outer liquid distributor 10 is used for uniformly distributing liquid on the outer wall surface of the heat transfer tube 9, and the liquid flows on the outer wall surface of the heat transfer tube 9 from top to bottom to be heated due to self gravity after passing through the outer liquid distributor 10; the solution regeneration cavity 7 realizes the process that the dilute solution on the outer surface of the heat transfer pipe 9 is heated to become concentrated solution and releases refrigerant steam in the process of flowing from top to bottom, the generated concentrated solution enters a concentrated solution pipeline 22, and the generated refrigerant steam enters a refrigerant (steam state) pipeline 19; the process of changing the liquid refrigerant into the vapor refrigerant is realized by the refrigerant evaporation cavity 6, the liquid refrigerant enters from the refrigerant (liquid) pipeline 17, flows from top to bottom on the outer wall surface of the heat transfer tube 9 after passing through the outer tube liquid distributor 10, is heated by the heat transfer tube 9 in the flowing process and changes from the liquid state into the vapor state, and the generated vapor state refrigerant enters into the refrigerant (vapor state) pipeline 21.
The heat pump unit comprises three internal working medium circulation loops: the non-azeotropic working medium circulation loop, the solution circulation loop and the refrigerant circulation loop are formed; the non-azeotropic working medium circulation loop comprises an evaporator 1, an electric compressor 2, a non-azeotropic working medium condensation cavity 8, a heat transfer pipe 9, a throttle valve 14 and a connecting pipeline; the liquid non-azeotropic working medium is heated by a waste heat water pipeline 15 in the evaporator to become a vapor state, then enters the electric compressor 2 to be further raised in temperature and pressure, the heat release of the non-azeotropic working medium after the temperature rise and the pressure rise in the channels of all the heat transfer pipes 9 in the condensation-evaporation-regeneration heat exchanger 3 is changed from the vapor state to the liquid state, then enters a non-azeotropic working medium (liquid) pipeline 16, and enters the evaporator 1 to complete the circulation of the non-azeotropic working medium after the temperature reduction and the pressure reduction of the throttle valve 14; the solution circulation loop comprises an absorber 5, a solution regeneration cavity 7, a heat transfer pipe 9, a solution heat exchanger 11, a solution pump 13 and a connecting pipeline; the concentrated solution enters the absorber 5 through the concentrated solution pipeline 22, and the concentration of the vapor refrigerant from the refrigerant (vapor) pipeline 21 is reduced after the vapor refrigerant is absorbed, and the heat is released to heat the medium to be heated in the heated medium pipeline 23; the dilute solution enters the dilute solution pipeline 24, passes through the solution heat exchanger 11 and then enters the solution regeneration cavity 7, flows on the outer wall surface of the heat transfer pipe 9 due to the action of gravity after passing through the external liquid distributor 10, is heated by the heat transfer pipe 9 to separate out refrigerant steam in the flowing process, and is concentrated into the concentrated solution, and the concentrated solution enters the concentrated solution pipeline 22, passes through the solution heat exchanger 11 and the solution pump 13 and then enters the absorber 5 to complete the solution circulation; the refrigerant circulation loop consists of a solution regeneration cavity 7, a condenser 4, a refrigerant evaporation cavity 6, a refrigerant pump 12 and connecting pipelines, wherein refrigerant vapor precipitated in the solution regeneration cavity 7 enters the condenser 4 through a refrigerant (vapor state) pipeline 19, the vapor state refrigerant is cooled by a cooling medium pipeline 18 and then is changed into a liquid state, the liquid state refrigerant enters the refrigerant evaporation cavity 6 after passing through the refrigerant pump 12 again, the liquid state refrigerant flows from top to bottom on the outer wall surface of the heat transfer tube 9 by gravity after passing through the external liquid distributor 10 and is heated into a vapor state, and the vapor state refrigerant enters the absorber 5 after entering the refrigerant (vapor state) pipeline 21 and is absorbed by the concentrated solution.
The non-azeotropic working medium adopted by the heat pump unit is HD-01 type super-temperature ternary non-azeotropic environment-friendly working medium with excellent thermophysical properties; the environment-friendly non-azeotropic working medium can realize that the condensation temperature exceeds 130 ℃, and has higher COP (coefficient of performance) under the same working condition compared with the pure working medium such as R245 fa; the HD-01 non-azeotropic working medium adopts a ternary mixture of R1234ze, R227ea and R245fa, wherein the mass fraction of the R1234ze in the ternary mixture ranges from 10% to 35%, the mass fraction of the R227ea ranges from 5% to 40%, and the mass fraction of the R245fa ranges from 40% to 85%;
r1234ze, formula chf=chcf3, CAS number 1645-83-6, critical temperature 109.37 ℃, ODP value 0;
r227ea, chemical formula CF3CHFCF3, CAS number 431-89-0, critical temperature 101.75 ℃, ODP value 0;
r245fa, formula CF3CH2CHF2, CAS number 460-73-1, critical temperature 154.01 ℃, ODP value 0.
Compared with the prior art, the HD-01 non-azeotropic working medium used in the invention has the following beneficial effects:
(1) The pure working medium ODP adopted by the preparation of the non-azeotropic working medium is 0, and belongs to environment-friendly working media;
(2) The non-azeotropic working medium has better temperature sliding property, and has higher COP compared with the existing non-azeotropic working medium when the temperature difference between the evaporating temperature and the condensing temperature is larger;
(3) The non-azeotropic working medium has better intersolubility with mineral oil, naphthenic oil, POE oil and the like;
(4) The non-azeotropic working medium has better compatibility with metal materials and nonmetal materials.
Drawings
FIG. 1 is a schematic flow chart of an ultra-high temperature non-azeotropic working medium heat pump set.
Reference numerals: 1-evaporator, 2-electric compressor, 3-condensation-evaporation-regeneration heat exchanger, 4-condenser, 5-absorber, 6-refrigerant evaporation cavity, 7-solution regeneration cavity, 8-zeotropic working medium condensation cavity, 9-heat transfer tube, 10-off-tube liquid distributor, 11-solution heat exchanger, 12-refrigerant pump, 13-solution pump, 14-throttle valve, 15-waste heat water pipeline, 16-zeotropic working medium (liquid) pipeline, 17-refrigerant (liquid) pipeline, 18-cooling medium pipeline, 19-refrigerant (vapor state) pipeline, 20-zeotropic working medium (vapor state) pipeline, 21-refrigerant (vapor state) pipeline, 22-concentrated solution pipeline, 23-heated medium pipeline, 24-dilute solution pipeline.
Detailed description of the preferred embodiments
In order to make the implementation objects, technical solutions and advantages of the present invention more clear, the technical solutions in the embodiments of the present invention will be described in more detail below with reference to the accompanying drawings in the embodiments of the present invention; in the drawings, like or similar reference numerals refer to like or similar elements throughout or elements having like or similar functions; the described embodiments are some, but not all, embodiments of the invention; the embodiments described below by referring to the drawings are intended to illustrate the invention and are not to be construed as limiting the invention; 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.
An ultra-high temperature non-azeotropic working medium heat pump unit comprises an evaporator 1, a condenser 4, a condensation-evaporation-regeneration heat exchanger 3, an absorber 5, an electric compressor 2, a circulating pump throttle valve and other accessories; the heat pump unit comprises three internal working medium circulation loops: the non-azeotropic working medium circulation loop, the solution circulation loop and the refrigerant circulation loop are formed; the working medium used in the non-azeotropic working medium circulation loop is an HD-01 ternary working medium, the HD-01 non-azeotropic working medium adopts a ternary mixture of R1234ze, R227ea and R245fa, the mass fraction of R1234ze in the ternary mixture ranges from 10% to 35%, the mass fraction of R227ea ranges from 5% to 40%, and the mass fraction of R245fa ranges from 40% to 85%; the proportion of the three components is matched according to the actual working temperature of the heat pump; the circulating working medium adopted by the solution circulating loop and the refrigerant circulating loop is an absorbent-refrigerant working medium pair which can be used by an absorption heat pump, and salt solutions such as lithium bromide-water, lithium chloride-water, lithium iodide-water and the like (water is used as a refrigerant, salts are used as an absorbent and mixed with the absorbent to form a solution), or lithium bromide-methanol, lithium bromide-trifluoroethanol and the like (alcohols are used as refrigerants, salts are used as an absorbent and mixed with the absorbent to form a solution), or trifluoro dichloroethane-dimethanol tetraethylene glycol and the like (freon is used as a refrigerant, alcohols are used as an absorbent and mixed with the absorbent to form a solution); the type of solution used is selected according to the operating temperature of the heat pump, and the implementation mode is described by using common lithium bromide-water as working medium.
The evaporator 1 of the heat pump unit is communicated with the condensing-evaporating-regenerating heat exchanger 3 through a pipeline, the condenser 4 is communicated with the condensing-evaporating-regenerating heat exchanger 3 through a pipeline, and the absorber 5 is communicated with the condensing-evaporating-regenerating heat exchanger 3 through a pipeline.
The connecting pipeline of the evaporator 1 of the heat pump comprises a waste heat water pipeline 15, a non-azeotropic working medium (liquid state) pipeline 16 and a non-azeotropic working medium (vapor state) pipeline 20; the liquid zeotropic working medium is vaporized from liquid state to vapor state after entering the evaporator 1 through the zeotropic working medium (liquid) pipeline 16 and being heated by the industrial waste heat medium in the waste heat water pipeline 15, and then the vapor state zeotropic working medium enters the zeotropic working medium (vapor state) pipeline 20 and leaves the evaporator 1 and then enters the electric compressor 2.
The connecting pipelines of the absorber 5 of the heat pump comprise a refrigerant (steam state) pipeline 21, a dilute solution pipeline 24, a concentrated solution pipeline 22 and a heated medium pipeline 23; the concentrated lithium bromide solution is fed into the absorber 5 to absorb water vapor from the refrigerant (vapor state) pipeline 21 in the flowing process, and the concentration of the lithium bromide solution is reduced and simultaneously heat is released in the absorbing process, and the heat is used for heating the medium (water, water vapor or other chemical fluid to be heated) in the pipeline 23 of the heated medium; the lithium bromide dilute solution that has finally completed the absorption process leaves the absorber 5 through dilute solution line 24.
The connecting lines of the condenser 4 of the heat pump comprise a refrigerant (vapour) line 19, a refrigerant (liquid) line 17 and a cooling medium line 18; the water vapor is cooled by heat exchange with the cooling medium line 18 after entering the condenser 4 through the refrigerant (vapor) line 19, and then the water vapor is changed from vapor to liquid, and the liquid water enters the refrigerant (liquid) line 17 and leaves the condenser 4.
The condensation-evaporation-regeneration heat exchanger 3 of the heat pump comprises a non-azeotropic working medium condensation cavity 8, a refrigerant evaporation cavity 6 and a solution regeneration cavity 7; the connecting pipelines of the condensation-evaporation-regeneration heat exchanger 3 comprise a non-azeotropic working medium (vapor state) pipeline 20, a refrigerant (liquid state) pipeline 17, a refrigerant (vapor state) pipeline 21, a non-azeotropic working medium (liquid state) pipeline 16, a dilute solution pipeline 24, a concentrated solution pipeline 22 and a refrigerant (vapor state) pipeline 19; the condensation-evaporation-regeneration heat exchanger 3 simultaneously realizes the heat exchange process of non-azeotropic working medium condensation, lithium bromide dilute solution regeneration and liquid water evaporation; the non-azeotropic working medium condensation cavity 8 inside the condensation-evaporation-regeneration heat exchanger 3 realizes the condensation process that the vapor state HD-01 working medium from the non-azeotropic working medium (vapor state) pipeline 20 changes from gas phase to liquid phase in the space in the heat transfer pipe 9, and the liquid HD-01 working medium formed by condensation enters the non-azeotropic working medium (liquid state) pipeline 16; the outer liquid distributor 10 is used for uniformly distributing liquid on the outer wall surface of the heat transfer tube 9, and the liquid flows on the outer wall surface of the heat transfer tube 9 from top to bottom to be heated due to self gravity after passing through the outer liquid distributor 10; the solution regeneration cavity 7 realizes the process that the lithium bromide dilute solution on the outer surface of the heat transfer pipe 9 is heated to become lithium bromide concentrated solution and releases water vapor in the process of flowing from top to bottom, the generated lithium bromide concentrated solution enters a concentrated solution pipeline 22, and the generated water vapor enters a refrigerant (vapor state) pipeline 19; the process of changing liquid water into water vapor is realized by the refrigerant evaporation cavity 6, the liquid water enters from the refrigerant (liquid) pipeline 17, flows from top to bottom on the outer wall surface of the heat transfer tube 9 after passing through the outside-tube liquid distributor 10, is heated by the heat transfer tube 9 to change from liquid to water vapor in the flowing process, and the generated water vapor enters into the refrigerant (vapor) pipeline 21.
The heat pump unit comprises three internal working medium circulation loops: a non-azeotropic working medium circulation loop, a lithium bromide solution circulation loop and a refrigerant water circulation loop; the non-azeotropic working medium circulation loop comprises an evaporator 1, an electric compressor 2, a non-azeotropic working medium condensation cavity 8, a heat transfer pipe 9, a throttle valve 14 and a connecting pipeline; the liquid HD-01 working medium is heated by a waste heat water pipeline 15 in the evaporator to become a vapor state, then enters the electric compressor 2 to be further raised in temperature and pressure, the heat release of the channels in all the heat transfer pipes 9 in the condensing-evaporating-regenerating heat exchanger 3 of the HD-01 working medium after the temperature and the pressure are raised is changed from the vapor state to the liquid state, then enters a non-azeotropic working medium (liquid) pipeline 16, and enters the evaporator 1 to complete the circulation of the HD-01 working medium after the temperature and the pressure are reduced by a throttle valve 14; the lithium bromide solution circulation loop comprises an absorber 5, a solution regeneration cavity 7, a heat transfer pipe 9, a solution heat exchanger 11, a solution pump 13 and a connecting pipeline; the lithium bromide concentrated solution enters the absorber 5 through the concentrated solution pipeline 22, absorbs the water vapor from the refrigerant (vapor state) pipeline 21, reduces the concentration, and simultaneously releases heat to heat the medium (water, water vapor or other chemical medium) to be heated in the heated medium pipeline 23; the lithium bromide dilute solution enters the dilute solution pipeline 24, passes through the solution heat exchanger 11 and then enters the solution regeneration cavity 7, flows on the outer wall surface of the heat transfer pipe 9 due to the action of gravity after passing through the external liquid distributor 10, is heated by the heat transfer pipe 9 to separate out water vapor in the flowing process, and is concentrated into the concentrated solution, and the lithium bromide concentrated solution enters the concentrated solution pipeline 22, passes through the solution heat exchanger 11 and the solution pump 13 and then enters the absorber 5 to complete the solution circulation; the refrigerant water circulation loop comprises a solution regeneration cavity 7, a condenser 4, a refrigerant evaporation cavity 6, a refrigerant pump 12 and connecting pipelines, wherein water vapor precipitated in the solution regeneration cavity 7 enters the condenser 4 through a refrigerant (vapor state) pipeline 19, the water vapor is cooled by a cooling medium pipeline 18 and then is changed into liquid water, the liquid water enters a refrigerant (liquid state) pipeline 17 and then enters the refrigerant evaporation cavity 6 after passing through the refrigerant pump 12, the liquid water flows from top to bottom under the action of gravity on the outer wall surface of a heat transfer pipe 9 after passing through an external liquid distributor 10 and is heated into the water vapor, and the water vapor enters a refrigerant (vapor state) pipeline 21 and then enters an absorber 5 and is absorbed by concentrated solution.
Finally, it should be pointed out that: the above embodiments are only for illustrating the technical solution of the present invention, and are not limiting; although the invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present invention.
Claims (6)
1. An ultra-high temperature non-azeotropic working medium heat pump unit is characterized in that: the heat pump unit includes: the evaporator (1), the condenser (4), the condensing-evaporating-regenerating heat exchanger (3), the absorber (5), the electric compressor (2), the throttle valve of the circulating pump and other accessories are formed;
the evaporator (1) of the heat pump unit is communicated with the condensation-evaporation-regeneration heat exchanger (3) through a pipeline, the condenser (4) is communicated with the condensation-evaporation-regeneration heat exchanger (3) through a pipeline, and the absorber (5) is communicated with the condensation-evaporation-regeneration heat exchanger (3) through a pipeline;
the connecting pipeline of the evaporator (1) of the heat pump comprises a waste heat water pipeline (15), a non-azeotropic working medium pipeline (16) and a non-azeotropic working medium pipeline (20); the liquid non-azeotropic working medium enters the evaporator (1) through a non-azeotropic working medium pipeline (16) and is heated by an industrial waste heat medium in a waste heat water pipeline (15) to be vaporized to be changed into a vapor state from the liquid state, and then the vapor state non-azeotropic working medium enters a non-azeotropic working medium pipeline (20) and leaves the evaporator 1 and enters the electric compressor (2);
the connecting pipeline of the absorber (5) of the heat pump comprises a refrigerant pipeline (21), a dilute solution pipeline (24), a concentrated solution pipeline (22) and a heated medium pipeline (23); the concentrated solution is absorbed by refrigerant steam from the refrigerant pipeline (21) in the flowing process after entering the absorber (5), and the concentration of the solution is reduced and heat is released in the absorbing process, and the heat is used for heating the medium in the pipeline of the heated medium pipeline (23); finally, the dilute solution which completes the absorption process leaves the absorber (5) through a dilute solution pipeline (24);
the connecting pipeline of the condenser (4) of the heat pump comprises a refrigerant pipeline (19), a refrigerant pipeline (17) and a cooling medium pipeline (18); the refrigerant steam enters the condenser (4) through the refrigerant pipeline (19) and then exchanges heat with the cooling medium pipeline (18) to be cooled, so that the refrigerant steam is changed into liquid state from vapor state, and the liquid state refrigerant enters the refrigerant pipeline (17) and leaves the condenser (4);
the condensation-evaporation-regeneration heat exchanger (3) of the heat pump is connected with the evaporator (1) through a non-azeotropic working medium pipeline (20) and a non-azeotropic working medium pipeline (16); the condensing-evaporating-regenerating heat exchanger (3) is connected with the absorber (5) through a dilute solution pipeline (24), a concentrated solution pipeline (22) and a refrigerant pipeline (21); the condensing-evaporating-regenerating heat exchanger (3) is connected with the condenser (4) through a refrigerant pipeline (19) and a refrigerant pipeline (17).
2. The ultra-high temperature non-azeotropic working medium heat pump unit according to claim 1, wherein: the condensation-evaporation-regeneration heat exchanger (3) of the heat pump comprises a non-azeotropic working medium condensation cavity (8), a refrigerant evaporation cavity (6) and a solution regeneration cavity (7); the connecting pipeline of the condensing-evaporating-regenerating heat exchanger (3) comprises a non-azeotropic working medium pipeline (20), a refrigerant pipeline (17), a refrigerant pipeline (21), a non-azeotropic working medium pipeline (16), a dilute solution pipeline (24), a concentrated solution pipeline (22) and a refrigerant pipeline (19); the condensation-evaporation-regeneration heat exchanger (3) simultaneously realizes the heat exchange process of non-azeotropic working medium condensation, dilute solution regeneration and liquid refrigerant evaporation; a non-azeotropic working medium condensation cavity (8) in the condensation-evaporation-regeneration heat exchanger (3) realizes the condensation process that the vapor non-azeotropic working medium from a non-azeotropic working medium pipeline (20) changes from gas phase to liquid phase in the space in the heat transfer pipe (9), and the liquid non-azeotropic working medium formed by condensation enters the non-azeotropic working medium pipeline (16); the external liquid distributor (10) is used for uniformly distributing liquid on the outer wall surface of the heat transfer tube (9), and the liquid flows on the outer wall surface of the heat transfer tube (9) from top to bottom due to self gravity after passing through the external liquid distributor (10) and is heated; the solution regeneration cavity (7) realizes the process that the dilute solution on the outer surface of the heat transfer pipe (9) is heated to become a concentrated solution and releases refrigerant steam in the process of flowing from top to bottom, the generated concentrated solution enters a concentrated solution pipeline (22), and the generated refrigerant steam enters a refrigerant pipeline (19); the process that the liquid refrigerant is changed into the vapor refrigerant is realized by the refrigerant evaporation cavity (6), the liquid refrigerant enters from the refrigerant pipeline (17), flows from top to bottom on the outer wall surface of the heat transfer pipe (9) after passing through the external liquid distributor (10), is heated by the heat transfer pipe (9) in the flowing process and is changed into the vapor state from the liquid state, and the generated vapor state refrigerant enters into the refrigerant pipeline (21).
3. The ultra-high temperature non-azeotropic working medium heat pump assembly according to claim 2, wherein: the heat pump unit comprises three internal working medium circulation loops: the non-azeotropic working medium circulation loop, the solution circulation loop and the refrigerant circulation loop are formed; the non-azeotropic working medium circulation loop comprises an evaporator (1), an electric compressor (2), a non-azeotropic working medium condensation cavity (8), a heat transfer pipe (9), a throttle valve (14) and a connecting pipeline; the liquid non-azeotropic working medium is heated by a waste heat water pipeline (15) in the evaporator to become a vapor state, then enters an electric compressor (2) to be further increased in temperature and pressure, the heat release of the non-azeotropic working medium after the temperature increase and the pressure increase in the channels of all heat transfer pipes (9) in the condensation-evaporation-regeneration heat exchanger (3) is changed from the vapor state to the liquid state, then enters a non-azeotropic working medium pipeline (16), and enters the evaporator (1) to complete the circulation of the non-azeotropic working medium after the temperature reduction and the pressure reduction of a throttle valve (14); the solution circulation loop comprises an absorber (5), a solution regeneration cavity (7), a heat transfer pipe (9), a solution heat exchanger (11), a solution pump (13) and a connecting pipeline; the concentrated solution enters the absorber (5) through the concentrated solution pipeline (22), the concentration of the vapor refrigerant from the refrigerant pipeline (21) is reduced after the vapor refrigerant is absorbed, and the heat is released to heat the medium to be heated in the heated medium pipeline (23); the dilute solution enters a dilute solution pipeline (24) and then enters a solution regeneration cavity (7) after passing through a solution heat exchanger (11), the dilute solution flows on the outer wall surface of a heat transfer pipe (9) due to the action of gravity after passing through an external liquid distributor (10), the refrigerant steam is heated and separated out by the heat transfer pipe (9) in the flowing process, meanwhile, the dilute solution is concentrated into a concentrated solution, and the concentrated solution enters a concentrated solution pipeline (22) and then enters an absorber (5) after passing through the solution heat exchanger (11) and a solution pump (13) to complete the solution circulation; the refrigerant circulation loop consists of a solution regeneration cavity (7), a condenser (4), a refrigerant evaporation cavity (6), a refrigerant pump (12) and a connecting pipeline, wherein refrigerant vapor separated out from the solution regeneration cavity (7) enters the condenser (4) through a refrigerant pipeline (19), the vaporous refrigerant is cooled by a cooling medium pipeline (18) and then is changed into liquid state from vapor state, the liquid refrigerant enters the refrigerant evaporation cavity (6) after passing through the refrigerant pump (12) again, the liquid refrigerant passes through an off-pipe liquid distributor (10) and then flows from top to bottom on the outer wall surface of a heat transfer pipe (9) by gravity to be heated into vapor state, and the vapor state refrigerant enters an absorber (5) to be absorbed by concentrated solution after entering the refrigerant pipeline (21).
4. The ultra-high temperature non-azeotropic working medium heat pump assembly according to claim 3, wherein: the non-azeotropic working medium adopted by the non-azeotropic working medium circulation loop is HD-01 ternary non-azeotropic environment-friendly working medium with excellent thermophysical properties; the HD-01 non-azeotropic working medium adopts a ternary mixture of R1234ze, R227ea and R245fa, wherein the mass fraction of the R1234ze in the ternary mixture ranges from 10% to 35%, the mass fraction of the R227ea ranges from 5% to 40%, and the mass fraction of the R245fa ranges from 40% to 85%.
5. The ultra-high temperature non-azeotropic working medium heat pump assembly according to claim 3, wherein: the solution adopted by the solution circulation loop is a working medium pair formed by combining an absorbent and a refrigerant, and the working medium pair adopts inorganic salt-water, inorganic salt-alcohols or freon-alcohols.
6. The ultra-high temperature non-azeotropic working medium heat pump unit according to claim 1, wherein: the condensation-evaporation-regeneration heat exchanger (3) realizes three heat exchange processes of non-azeotropic working medium condensation in the pipe, solution regeneration outside the pipe and refrigerant evaporation at the same time.
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| CN110057128B (en) * | 2019-05-29 | 2023-12-19 | 北京华电东晟科技有限公司 | Coupling heat pump heat exchanger |
| CN110806038B (en) * | 2019-11-27 | 2021-07-27 | 江苏天舒电器有限公司 | Control method of heat pump system for dehumidification and drying |
| CN111336685B (en) * | 2020-04-09 | 2024-06-11 | 华北电力大学 | Super heat pump |
| CN114350321B (en) * | 2021-12-03 | 2024-02-09 | 湖北瑞能华辉能源管理有限公司 | Energy-saving environment-friendly heat pump working medium and application thereof |
Citations (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4285211A (en) * | 1978-03-16 | 1981-08-25 | Clark Silas W | Compressor-assisted absorption refrigeration system |
| US4327555A (en) * | 1979-09-10 | 1982-05-04 | Dimon Donald F | Solar air conditioning system |
| JPS63131962A (en) * | 1986-11-21 | 1988-06-03 | 日立造船株式会社 | Solid absorption heat pump |
| CN1055421A (en) * | 1991-05-25 | 1991-10-16 | 北京化工学院 | Falling-film absorption type heat pump |
| US5161382A (en) * | 1991-05-24 | 1992-11-10 | Marin Tek, Inc. | Combined cryosorption/auto-refrigerating cascade low temperature system |
| JPH06147681A (en) * | 1992-11-02 | 1994-05-27 | Honda Motor Co Ltd | Absorber/condenser for air-cooled absorption refrigerator |
| US5896747A (en) * | 1995-08-01 | 1999-04-27 | Antohi; Valentin | Vehicular absorption air conditioning process and system utilizing engine coolant waste heat |
| JP2002206818A (en) * | 2001-01-12 | 2002-07-26 | Minoru Morita | Absorbing type heat pump device |
| JP2003056937A (en) * | 2001-08-09 | 2003-02-26 | Sekisui Chem Co Ltd | Heat pump system |
| CN1865813A (en) * | 2006-05-10 | 2006-11-22 | 江苏双良空调设备股份有限公司 | Second lithium bromide absorption type heat pump for preparing steam by using vertical double-side falling-film absorber |
| CN101055136A (en) * | 2007-06-01 | 2007-10-17 | 浙江大学 | Low grade energy driven and mechanical power driven composite heat pump, refrigeration system |
| CN101329118A (en) * | 2008-07-23 | 2008-12-24 | 清华大学 | Compact type absorption heat pump apparatus capable of increasing residual heat temperature greatly |
| JP2009168271A (en) * | 2008-01-11 | 2009-07-30 | Japan Steel Works Ltd:The | Double effect absorption type cold and heat generating/outputting device |
| CN101726058A (en) * | 2009-11-20 | 2010-06-09 | 青岛海科节能工程技术有限公司 | Integrated solution type dehumidifying air-conditioning device |
| JP2010216793A (en) * | 2009-03-16 | 2010-09-30 | Masahisa Fujimoto | Absorption cooler and heat exchanger |
| CN105180507A (en) * | 2015-09-23 | 2015-12-23 | 内蒙古科技大学 | Self-overlapping vortex tube absorbing refrigerating system |
| CN205048524U (en) * | 2015-03-17 | 2016-02-24 | 哈尔滨工大金涛科技股份有限公司 | Temperature of heat supply network return water is reduced big difference in temperature heat transfer device |
| CN107869857A (en) * | 2017-11-07 | 2018-04-03 | 北京拓首能源科技股份有限公司 | One kind is based on the second kind absorption type mixing heat pump |
| CN108061400A (en) * | 2017-08-28 | 2018-05-22 | 浙江大学 | A kind of changeable two-way mixed working fluid heat pump system |
| CN110220303A (en) * | 2019-02-26 | 2019-09-10 | 华北电力大学 | A kind of low * damage heat exchanger |
| CN209371561U (en) * | 2018-09-06 | 2019-09-10 | 华北电力大学 | A kind of superhigh temperature non-azeotropic working medium heat pump unit |
-
2018
- 2018-09-06 CN CN201811036483.5A patent/CN108844253B/en active Active
Patent Citations (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4285211A (en) * | 1978-03-16 | 1981-08-25 | Clark Silas W | Compressor-assisted absorption refrigeration system |
| US4327555A (en) * | 1979-09-10 | 1982-05-04 | Dimon Donald F | Solar air conditioning system |
| JPS63131962A (en) * | 1986-11-21 | 1988-06-03 | 日立造船株式会社 | Solid absorption heat pump |
| US5161382A (en) * | 1991-05-24 | 1992-11-10 | Marin Tek, Inc. | Combined cryosorption/auto-refrigerating cascade low temperature system |
| CN1055421A (en) * | 1991-05-25 | 1991-10-16 | 北京化工学院 | Falling-film absorption type heat pump |
| JPH06147681A (en) * | 1992-11-02 | 1994-05-27 | Honda Motor Co Ltd | Absorber/condenser for air-cooled absorption refrigerator |
| US5896747A (en) * | 1995-08-01 | 1999-04-27 | Antohi; Valentin | Vehicular absorption air conditioning process and system utilizing engine coolant waste heat |
| JP2002206818A (en) * | 2001-01-12 | 2002-07-26 | Minoru Morita | Absorbing type heat pump device |
| JP2003056937A (en) * | 2001-08-09 | 2003-02-26 | Sekisui Chem Co Ltd | Heat pump system |
| CN1865813A (en) * | 2006-05-10 | 2006-11-22 | 江苏双良空调设备股份有限公司 | Second lithium bromide absorption type heat pump for preparing steam by using vertical double-side falling-film absorber |
| CN101055136A (en) * | 2007-06-01 | 2007-10-17 | 浙江大学 | Low grade energy driven and mechanical power driven composite heat pump, refrigeration system |
| JP2009168271A (en) * | 2008-01-11 | 2009-07-30 | Japan Steel Works Ltd:The | Double effect absorption type cold and heat generating/outputting device |
| CN101329118A (en) * | 2008-07-23 | 2008-12-24 | 清华大学 | Compact type absorption heat pump apparatus capable of increasing residual heat temperature greatly |
| JP2010216793A (en) * | 2009-03-16 | 2010-09-30 | Masahisa Fujimoto | Absorption cooler and heat exchanger |
| CN101726058A (en) * | 2009-11-20 | 2010-06-09 | 青岛海科节能工程技术有限公司 | Integrated solution type dehumidifying air-conditioning device |
| CN205048524U (en) * | 2015-03-17 | 2016-02-24 | 哈尔滨工大金涛科技股份有限公司 | Temperature of heat supply network return water is reduced big difference in temperature heat transfer device |
| CN105180507A (en) * | 2015-09-23 | 2015-12-23 | 内蒙古科技大学 | Self-overlapping vortex tube absorbing refrigerating system |
| CN108061400A (en) * | 2017-08-28 | 2018-05-22 | 浙江大学 | A kind of changeable two-way mixed working fluid heat pump system |
| CN107869857A (en) * | 2017-11-07 | 2018-04-03 | 北京拓首能源科技股份有限公司 | One kind is based on the second kind absorption type mixing heat pump |
| CN209371561U (en) * | 2018-09-06 | 2019-09-10 | 华北电力大学 | A kind of superhigh temperature non-azeotropic working medium heat pump unit |
| CN110220303A (en) * | 2019-02-26 | 2019-09-10 | 华北电力大学 | A kind of low * damage heat exchanger |
Non-Patent Citations (1)
| Title |
|---|
| 孙健 ; 王寅武 ; 吴可欣 ; 陶建龙 ; 秦宇.新型吸收式与压缩式耦合循环性能研究.《太阳能学报》.2020,375-379. * |
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