CN109425143A - Absorption type heat exchange system - Google Patents
Absorption type heat exchange system Download PDFInfo
- Publication number
- CN109425143A CN109425143A CN201810902236.2A CN201810902236A CN109425143A CN 109425143 A CN109425143 A CN 109425143A CN 201810902236 A CN201810902236 A CN 201810902236A CN 109425143 A CN109425143 A CN 109425143A
- Authority
- CN
- China
- Prior art keywords
- mentioned
- fluid
- heat
- exchange system
- heat exchange
- 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.)
- Pending
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
- F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/62—Absorption based systems
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 present invention provides the absorption type heat exchange system (1) for making simplified, has: condensation part (40) rise the temperature for being heated fluid (TS) using the condensation heat of refrigerant vapour (Vg)；Evaporation part (20) reduces the temperature of the first heating source fluid (TP) using the evaporation latent heat of refrigerant liquid (Vf)；Absorption portion (10), absorption heat when absorbing refrigerant vapour (Ve) using absorbing liquid (Sa) rise the temperature for being heated fluid；With reproducing unit (30), from the second heating source fluid (HP) capture heat dilute solution needed for heat, it is configured to recycle by the sorption type heat pump of absorbing liquid (Sa, Sw) and refrigerant (Ve, Vf, Vg), the pressure and temperature of absorption portion and the evaporation part inside compared with reproducing unit and condensation part is low, and a part for being heated fluid branch before being fed to condensation part and absorption portion is heated fluid as the first heating source fluid and is directed into evaporation part.
Description
Technical field
The present invention relates to absorption type heat exchange systems, in particular to make the absorption heat exchange series of simplified
System.
Background technique
It is drawn in hot machine that is, heat pump to be heated to the medium of heating target as from the heat source of low temperature
The device of thermal drivers, there is known sorption type heat pumps.As the application examples of sorption type heat pump, there are it is a kind of include heat exchange such as lower component
Device: the warm water absorption heat pump with generator, evaporator, condenser and absorber；Water-water heat exchanger；Successively
By generator, water-water heat exchanger, evaporator a heat supply network pipeline；With by absorber, condenser and
The second heat supply network pipeline of water-water heat exchanger (for example, referring to patent document 1).
Patent document 1: No. 5194122 bulletins of Japanese Patent No.
The heat-exchange device as documented by patent document 1 is also equipped with water-hydro-thermal in addition to warm water other than absorption heat pump
Exchanger, so leading to device integrally becomes large-scale.
Summary of the invention
The present invention is exchanged in view of the above subject it is intended that providing a kind of absorption type heat for making simplified
System.
To achieve the goals above, absorption type heat exchange system involved in the 1st aspect of the present invention is for example such as Fig. 1 institute
Show have: condensation part 40, the condensation heat that discharges when becoming refrigerant liquid Vf by the steam Vg of refrigerant condensation make to be added
The temperature of hot fluid TS rises；Evaporation part 20 imports refrigerant liquid Vf from condensation part 40, by taking by force from the first heating source fluid TP
It takes imported refrigerant liquid Vf to evaporate and becomes evaporation latent heat required when refrigerant vapour Ve, to make the first heating source fluid
The temperature of TP reduces；Absorption portion 10 imports refrigerant vapour Ve from evaporation part 20, imported refrigeration is absorbed by absorbing liquid Sa
Agent steam Ve and absorption heat that while becoming the weak solution Sw that concentration reduces discharges rises to make to be heated the temperature of fluid TS；With
And reproducing unit 30, from absorption portion 10 import weak solution Sw, by from the second heating source fluid HP capture heating imported it is dilute molten
Heat needed for liquid Sw makes refrigerant Vg become the concentrated solution Sa that concentration rises from weak solution Sw disengaging, to make the second heating source
The temperature of fluid HP reduces, and above-mentioned absorption type heat exchange system is configured to through absorbing liquid Sa, Sw and refrigerant Ve, Vf, Vg
Sorption type heat pump circulation, absorption portion 10 pressure and temperature internal compared with reproducing unit 30 are low, evaporation part 20 and 40 phase of condensation part
It is lower than internal pressure and temperature, and be configured to that stream will be heated before being fed to condensation part 40 and absorption portion 10
A part of body TA branch is heated fluid as the first heating source fluid TP and is directed into evaporation part 20.
If constituting in this way, due to by be heated fluid branch one before being fed to condensation part and absorption portion
Part is heated fluid as the first heating source fluid and is directed into evaporation part, so the first heating source fluid flowed out from evaporation part
Temperature it is lower than the temperature for being heated fluid before being fed to condensation part and absorption portion, can make absorption type heat exchange
The heat swapped in system increases, and the first heating source stream can not be reduced by the heat exchanger of the first heating source fluid
The temperature of body can omit the heat exchanger of the first heating source fluid and simplify apparatus structure.
In addition, absorption type heat exchange system is at above-mentioned involved in the 2nd aspect of the present invention referring for example to shown in Fig. 1
On the basis of absorption type heat exchange system 1 involved in the first method of invention, be configured to flow out from reproducing unit 30 second adds
At least part of heat source fluid HP is mixed with the fluid TS that is heated flowed out from at least one party in condensation part 40 and absorption portion 10
It closes.
If in this way constitute, can either simplied system structure, and can effectively utilize in reproducing unit as heat source benefit
The heat possessed by the second heating source fluid later.
In addition, absorption type heat exchange system is at above-mentioned involved in the 3rd aspect of the present invention referring for example to shown in Fig. 1
On the basis of absorption type heat exchange system 1 involved in the second method of invention, it is configured to setting and flows into condensation part 40
And the flow for being heated fluid TS in absorption portion 10 flows into being heated for evaporation part 20 with as the first heating source fluid
The ratio between the flow of fluid TP so that at least part of the second heating source fluid HP flowed out from reproducing unit 30 with from condensation part 40
And the mixed mixing of fluid TS that is heated of at least one party's outflow in absorption portion 10 is heated the temperature of fluid TA as rule
Fixed temperature.
If constituting in this way, the temperature that mixing is heated fluid can be adjusted.
In addition, for example as shown in figure 5, absorption type heat exchange system involved in the 4th aspect of the present invention is sent out at above-mentioned
On the basis of absorption type heat exchange system 5 involved in bright second method or Third Way, be configured to from condensation part 40 with
And one from the second heating source fluid HP branch of at least one party's outflow in absorption portion 10 being heated before fluid TS mixing
Remaining second heating source fluid HP after point the second heating source fluid HP and branch with from condensation part 40 and absorption portion 10
The fluid TA that fluid TS is mixed that is heated of at least one party's outflow flows out with being individually separated from absorption type heat exchange system 5.
If constituting in this way, heat can be supplied to multiple places.
In addition, for example as shown in Fig. 2, absorption type heat exchange system is at above-mentioned involved in the 5th aspect of the present invention
The first method of invention on the basis of absorption type heat exchange system 2 involved in formula, has office either into fourth way
Portion's heating source bypass of fluid flow path 28, the localized heat source bypass of fluid flow path 28 make the second heating by flowing out from reproducing unit 30
A part the second heating source fluid HP of source stream body HP branch and the first heating source fluid TP being fed to before evaporation part 20
Converge.
If constituting in this way, the temperature of the first heating source fluid flowed out from evaporation part can be adjusted.
In addition, absorption type heat exchange system is at above-mentioned involved in the 6th aspect of the present invention referring for example to shown in Fig. 2
On the basis of absorption type heat exchange system 2 involved in 5th mode of invention, it is configured to setting and is flowed out from reproducing unit 30
The second heating source fluid HP the flow for not flowing into localized heat source bypass of fluid flow path 28 in localized heat source fluid
The ratio between the flow that bypass flow path 28 flows so that at least part of the second heating source fluid HP flowed out from reproducing unit 30 with from
The temperature for being heated the mixed mixing of fluid TS and being heated fluid TA of at least one party in condensation part 40 and absorption portion 10 outflow
Degree becomes defined temperature.
If constituting in this way, it can be heated the temperature of fluid to mixing and the balance of flow is adjusted.
In addition, for example, as shown in figure 4, absorption type heat exchange system involved in the 7th aspect of the present invention is sent out at above-mentioned
On the basis of absorption type heat exchange system 4 involved in the 5th bright mode or the 6th mode, it is configured to make in localized heat source
Bypass of fluid flow path 28 flow the second heating source fluid HP by heat utilization and temperature reduce after be fed to evaporation part
The first heating source fluid TP before 20 converges.
If constituting in this way, other than what is flowed out from condensation part or absorption portion is heated heat possessed by fluid, moreover it is possible to
It is enough to exchange heat supply possessed by the second heating source fluid in localized heat source bypass of fluid flow path to absorption type heat
The outside of system.
In addition, for example as shown in figure 3, absorption type heat exchange system involved in the 8th aspect of the present invention is sent out at above-mentioned
On the basis of absorption type heat exchange system 3 involved in bright first method, it is configured to the second heating flowed out from reproducing unit 30
At least part of source stream body HP with flowed out from condensation part 40 be heated fluid TS be individually separated from absorption heat exchange series
3 outflow of system.
It, can be by heat supply to multiple places if constituting in this way.
According to the present invention, due to by one for being heated fluid branch before being fed to condensation part and absorption portion
Point being heated fluid as the first heating source fluid is directed into evaporation part, so the first heating source fluid flowed out from evaporation part
Temperature it is lower than the temperature for being heated fluid before being fed to condensation part and absorption portion, can make absorption type heat exchange
The heat swapped in system increases, and the first heating source stream can not be reduced by the heat exchanger of the first heating source fluid
The temperature of body can omit the heat exchanger of the first heating source fluid and simplify apparatus structure.
Detailed description of the invention
Fig. 1 is the schematic system diagram of absorption type heat exchange system involved in first embodiment of the invention.
Fig. 2 is the schematic system diagram of absorption type heat exchange system involved in second embodiment of the present invention.
Fig. 3 is the schematic system diagram of absorption type heat exchange system involved in third embodiment of the present invention.
Fig. 4 is the schematic system diagram of absorption type heat exchange system involved in the 4th embodiment of the invention.
Fig. 5 is the schematic system diagram of absorption type heat exchange system involved in the 5th embodiment of the invention.
Description of symbols:
1,2,3,4,5 ... absorption type heat exchange system；10 ... absorbers；20 ... evaporators；28 ... high temperature heat source bypass pipes；
30 ... regenerators；40 ... condensers；Sa ... concentrated solution；Sw ... weak solution；HP ... high temperature heat source fluid；TP ... medium temperature heat source stream
Body；TS ... gain of heat subject fluid；Ve ... evaporator refrigerant steam；Vf ... refrigerant liquid；Vg ... regenerator refrigerant vapour.
Specific embodiment
Hereinafter, the embodiments of the present invention will be described with reference to the drawings.Wherein, in the various figures, to mutually the same or phase
When component mark same or similar appended drawing reference, and the repetitive description thereof will be omitted.
With reference first to Fig. 1, absorption type heat exchange system 1 involved in first embodiment of the invention is illustrated.
Fig. 1 is the schematic system diagram of absorption type heat exchange system 1.Absorption type heat exchange system 1 is to utilize absorbing liquid and refrigerant
Sorption type heat pump circulation makes heat from the fluid flowed into relative to heat resource equipment HSF outflow to relative to heat utilization equipment HCF flowing out stream
The system of the fluid transmitting entered.Absorption type heat exchange system 1 has absorber 10, evaporator 20, regenerator 30 and condenser
40, they, which are constituted, carries out the main machine that the sorption type heat pump of absorbing liquid S (Sa, Sw) and refrigerant V (Ve, Vg, Vf) recycles.It absorbs
Device 10, evaporator 20, regenerator 30 and condenser 40 are respectively equivalent to absorption portion, evaporation part, reproducing unit and condensation part.
In the present specification, it is followed to be easy difference on heat pump cycle according to property states, heat pump about absorbing liquid
Position on ring and be known as " weak solution Sw ", " concentrated solution Sa " etc., but when not considering property states etc., be referred to as " absorbing liquid
S".Equally, claimed to be easy difference on heat pump cycle according to the position on property states, heat pump cycle about refrigerant
For " evaporator refrigerant steam Ve ", " regenerator refrigerant vapour Vg ", " refrigerant liquid Vf " etc., but do not considering property states
" refrigerant V " is referred to as whens equal.In the present embodiment, use LiBr aqueous solution as absorbing liquid S (absorbent and refrigerant V
Mixture), use water (H2O) it is used as refrigerant V.
Absorber 10 includes heat-transfer pipe 12 in inside, constitutes the flow path of gain of heat subject fluid TS；With concentrated solution feedway
13, concentrated solution Sa is supplied to the surface of heat-transfer pipe 12.Heat-transfer pipe 12 is connected with gain of heat fluid ingress pipe 51 at one end, another
End is connected with gain of heat fluid connection tube 15.Gain of heat fluid ingress pipe 51 is to constitute to guide gain of heat subject fluid TS to heat-transfer pipe 12
Flow path pipe.Gain of heat fluid ingress pipe 51 is provided with gain of heat fluid valve 51v, gain of heat fluid valve 51v is in internal flow
The flow of gain of heat subject fluid TS be adjusted.Gain of heat fluid connection tube 15 is constituted the gain of heat heated by absorber 10
The pipe for the flow path that subject fluid TS is guided to condenser 40.Absorber 10 from concentrated solution feedway 13 by concentrated solution Sa supply to
The surface of heat-transfer pipe 12 generates when concentrated solution Sa absorbs evaporator refrigerant steam Ve and becomes weak solution Sw and absorbs heat.Structure
Receive absorption heat as the gain of heat subject fluid TS flowed in heat-transfer pipe 12, gain of heat subject fluid TS is heated.
Evaporator 20 includes heat source tube 22 in the inside of evaporator tank body 21, constitutes the flow path of medium temperature heat source fluid TP；With
Refrigerant liquid feedway 23 supplies refrigerant liquid Vf to the surface of heat source tube 22.In one end of heat source tube 22 is connected with
Temperature-heat-source ingress pipe 52.Middle temperature-heat-source ingress pipe 52 is to constitute to guide medium temperature heat source fluid TP to the flow path of heat source tube 22
Pipe.Middle temperature-heat-source ingress pipe 52 is provided with medium temperature heat source valve 52v, the medium temperature heat source valve 52v is to the middle warm in internal flow
The flow of source stream body TP is adjusted.The other end of the other end of middle temperature-heat-source ingress pipe 52 and gain of heat fluid ingress pipe 51 is together
Pipe 55 is flowed into fluid-mixing to connect.It is the pipe for constituting the flow path for fluid-mixing TA flowing that fluid-mixing, which flows into pipe 55,.It constitutes
It flows into gain of heat fluid ingress pipe 51 to flow into the fluid-mixing TA shunting that pipe 55 flows in fluid-mixing and is led with middle temperature-heat-source
Enter pipe 52.That is, gain of heat subject fluid TS is the fluid for flowing into gain of heat fluid ingress pipe 51 in fluid-mixing TA, middle temperature-heat-source
Fluid TP is the fluid for flowing into middle temperature-heat-source ingress pipe 52 in fluid-mixing TA.Heat source tube 22 be connected in warm
The end of the end opposite side of source ingress pipe 52 is connected with medium temperature heat source effuser 29.Medium temperature heat source effuser 29 is that composition will
Pipe of the medium temperature heat source fluid TP to the flow path guided except evaporator 20.Evaporator 20 is configured to from refrigerant liquid feedway 23
Refrigerant liquid Vf is supplied to the surface of heat source tube 22, the refrigerant liquid Vf on 22 periphery of heat source tube is utilized to be flowed in heat source tube 22
Medium temperature heat source fluid TP thermal evaporation and generate evaporator refrigerant steam Ve.Medium temperature heat source fluid TP is equivalent to the first heating
Source stream body.
Absorber 10 communicates with each other with evaporator 20.Be connected to by absorber 10 with evaporator 20, be configured to by
The evaporator refrigerant steam Ve that evaporator 20 generates is supplied to absorber 10.
Regenerator 30 includes heat source tube 32, for heat dilute solution Sw high temperature heat source fluid HP in internal flow；With it is dilute molten
Liquid supplying device 33 supplies weak solution Sw to the surface of heat source tube 32.High temperature heat source is connected in one end of heat source tube 32 to lead
Enter pipe 57, the high temperature heat source ingress pipe 57 composition guides high temperature heat source fluid HP to the flow path of heat source tube 32.In heat source tube 32
The other end be connected with one end of high temperature heat source effuser 39, which is constituted for flowing out from regenerator 30
The flow path of high temperature heat source fluid HP flowing.Regenerator 30 is configured to the weak solution Sw by will supply from weak solution feedway 33
It is heated into high temperature heat source fluid HP, thus generates the concentrated solution Sa that concentration rises from weak solution Sw evaporated refrigerant V.High warm
Source stream body HP is equivalent to the second heating source fluid.It is configured to the refrigerant V evaporated from weak solution Sw to steam as regenerator refrigerant
Vapour Vg is moved to condenser 40.
Condenser 40 has the heat-transfer pipe 42 flowed for gain of heat subject fluid TS in the inside of condenser tank body 41.It is conducting heat
The gain of heat subject fluid TS that pipe 42 flows becomes the gain of heat subject fluid TS after the heat-transfer pipe 12 of absorber 10 flows.It absorbs
The heat-transfer pipe 12 of device 10 and the heat-transfer pipe 42 of condenser 40 are connected by the gain of heat fluid connection tube 15 of flowing gain of heat subject fluid TS
It connects.With the end of the end opposite side for being connected with gain of heat fluid connection tube 15 increasing is connected in the heat-transfer pipe 42 of condenser 40
Hot fluid effuser 49.Gain of heat fluid effuser 49 is constituted gain of heat subject fluid TS to the flow path guided except condenser 40
Pipe.The other end of the other end of gain of heat fluid effuser 49 and high temperature heat source effuser 39 together with fluid-mixing effuser 59
Connection.Fluid-mixing effuser 59 is to constitute high temperature heat source fluid HP for flow in high temperature heat source effuser 39 and in gain of heat stream
Body effuser 49 flow gain of heat subject fluid TS converge after fluid-mixing TA flowing flow path pipe.Fluid-mixing TA is suitable
Fluid is heated in mixing.Condenser 40 is configured to import the regenerator refrigerant vapour Vg generated in regenerator 30, is passing
The release when gain of heat subject fluid TS flowed in heat pipe 42 receives regenerator refrigerant vapour Vg condensation and becomes refrigerant liquid Vf
Condensation heat, gain of heat subject fluid TS is heated.Gain of heat subject fluid TS, which is equivalent to, is heated fluid.With regenerator 30 and condensation
The mode that device 40 communicates with each other, tank body and the condenser tank body 41 of regenerator 30 are formed as one.It is configured to through regenerator 30
It is connected to condenser 40, thus, it is possible to the regenerator refrigerant vapour Vg that will be generated in regenerator 30 to supply to condenser 40.
The part of the storage concentrated solution Sa of regenerator 30 and the concentrated solution feedway 13 of absorber 10 are by for concentrated solution
The concentrated solution pipe 35 of Sa flowing connects.The part of the storage weak solution Sw of absorber 10 passes through with weak solution feedway 33 for dilute
The weak solution pipe 36 of solution S w flowing connects.The solution pump 36p of force feed weak solution Sw is equipped in weak solution pipe 36.In concentrated solution
Pipe 35 and weak solution pipe 36 are equipped with solution heat exchanger 38, the solution heat exchanger 38 concentrated solution Sa and weak solution Sw it
Between carry out heat exchange.The part of the storage refrigerant liquid Vf of condenser 40 is with refrigerant liquid feedway 23 by for refrigerant liquid
The refrigerant liquid pipe 45 of Vf flowing connects.
Absorption type heat exchange system 1 is in steady running, and the pressure and temperature of the inside of absorber 10 are than regenerator 30
Inside pressure and temperature it is low, the pressure and temperature of the inside of evaporator 20 than the inside of condenser 40 pressure and
Temperature is low.Absorber 10, evaporator 20, regenerator 30 and the condenser 40 of absorption type heat exchange system 1 are as the first suction
Receive the structure of heat pump.
In the present embodiment, high temperature heat source ingress pipe 57 and medium temperature heat source effuser 29 are connect with heat resource equipment HSF.
Heat resource equipment HSF is, for example, the heat pump of heating type.In the present embodiment, heat resource equipment HSF is to therefrom temperature-heat-source effuser 29
The medium temperature heat source fluid TP being taken into is heated rise temperature, is supplied as high temperature heat source fluid HP to high temperature heat source and is imported
Pipe 57.In the present embodiment, fluid-mixing effuser 59 and fluid-mixing flow into pipe 55 and connect with heat utilization equipment HCF.
Heat utilization equipment HCF is for example by the heat utilization of importing in heating.In the present embodiment, heat utilization equipment HCF is utilized from mixed
Collaborate heat possessed by the fluid-mixing TA that body effuser 59 imports, and makes to capture from fluid-mixing TA hot and temperature reduction mixed
Interflow body TA flows out to fluid-mixing and flows into pipe 55.
Then, the effect of absorption type heat exchange system 1 is illustrated referring to Fig.1.Firstly, to the sorption type heat pump of solution side
Circulation is illustrated.In absorber 10, concentrated solution Sa is supplied from concentrated solution feedway 13, the concentrated solution Sa of the supply absorbs
From the mobile next evaporator refrigerant steam Ve of evaporator 20.Absorb the concentrated solution Sa concentration drop of evaporator refrigerant steam Ve
It is low and become weak solution Sw.In absorber 10, concentrated solution Sa is generated when absorbing evaporator refrigerant steam Ve absorbs heat.Pass through
Absorption heat is heated in the gain of heat subject fluid TS that heat-transfer pipe 12 flows, and the temperature of gain of heat subject fluid TS rises.It is absorbing
The concentrated solution Sa concentration that device 10 absorbs evaporator refrigerant steam Ve reduces and becomes weak solution Sw, is stored in absorber 10
Lower part.Stored weak solution Sw is flowed towards regenerator 30 in weak solution pipe 36 by solution pump 36p force feed, in solution heat
Heat exchange is carried out in exchanger 38 with concentrated solution Sa, temperature rises, and then reaches regenerator 30.
It is delivered to the height that the weak solution Sw of regenerator 30 is supplied from weak solution feedway 33 and flowed in heat source tube 32
Temperature-heat-source fluid HP is heated, and the refrigerant in the weak solution Sw supplied evaporates and becomes concentrated solution Sa, is stored in regenerator 30
Lower part.At this point, high temperature heat source fluid HP by weak solution Sw capture heat and temperature reduce.The refrigerant V evaporated from weak solution Sw
It is mobile to condenser 40 as regenerator refrigerant vapour Vg.The concentrated solution Sa of the lower part of regenerator 30 is stored in because of regenerator 30
And the difference of the internal pressure of absorber 10 and via concentrated solution pipe 35 reach absorber 10 concentrated solution feedway 13.In concentrated solution pipe
The concentrated solution Sa of 35 flowings carries out heat exchange with weak solution Sw in solution heat exchanger 38 and temperature reduces, and flows into suction later
Device 10 is received, is supplied from concentrated solution feedway 13, after, repeat the circulation of above-mentioned absorbing liquid S.
Next the sorption type heat pump circulation of refrigerant side is illustrated.In condenser 40, receive in regenerator 30
Regenerator the refrigerant vapour Vg, the gain of heat subject fluid TS that regenerator refrigerant vapour Vg is flowed in heat-transfer pipe 42 of evaporation are cold
But it condenses, becomes refrigerant liquid Vf.At this point, gain of heat subject fluid TS is cold because discharging when regenerator refrigerant vapour Vg is condensed
Solidifying heat and temperature rises.Heat-transfer pipe 42 flow gain of heat subject fluid TS be by the heat-transfer pipe 12 of absorber 10 come stream
Body.Condensed refrigerant liquid Vf flows due to the difference of the internal pressure of condenser 40 and evaporator 20 in refrigerant liquid pipe 45, reaches
Evaporator 20.The refrigerant liquid Vf for being delivered to evaporator 20 is supplied from refrigerant liquid feedway 23, is flowed in heat source tube 22
Dynamic medium temperature heat source fluid TP heating, evaporates and becomes evaporator refrigerant steam Ve.At this point, medium temperature heat source fluid TP is freezed
Agent liquid Vf captures heat and temperature reduces.In the evaporator refrigerant steam Ve that evaporator 20 generates to the suction being connected to evaporator 20
It is mobile to receive device 10, after, repeat same circulation.
Enumerate specific example to absorbing liquid S and refrigerant V carry out it is during sorption type heat pump circulation as described above,
The variation for being heated the temperature of fluid and heating source fluid is illustrated.For flowing out and mixing from heat utilization equipment HCF
Fluid flows into for 40 DEG C of the fluid-mixing TA that pipe 55 flows, gain of heat subject fluid TS and medium temperature heat source fluid after shunting
TP is respectively 40 DEG C.In 40 DEG C of the gain of heat subject fluid TS that gain of heat fluid ingress pipe 51 flows when the heat-transfer pipe in absorber 10
When 12 flowing, the absorption heat that concentrated solution Sa absorbs evaporator refrigerant steam Ve and generates is obtained, if reaching the linking of gain of heat fluid
Then temperature rises to 45 DEG C to pipe 15.Then, work as in the gain of heat subject fluid TS that gain of heat fluid connection tube 15 flows in condenser 40
The condensation heat that discharges when becoming refrigerant liquid Vf that obtains regenerator refrigerant vapour Vg condensation when flowing of heat-transfer pipe 42, if reaching
Then temperature rises to 50 DEG C to gain of heat fluid effuser 49.
On the other hand, in the medium temperature heat source fluid TP of middle temperature-heat-source ingress pipe 52 flowing when the heat source tube 22 in evaporator 20
Heat is captured by refrigerant liquid Vf when flowing, temperature is reduced to 30 DEG C if reaching medium temperature heat source effuser 29.In medium temperature heat source stream
30 DEG C of the medium temperature heat source fluid TP that outlet pipe 29 flows flows into heat resource equipment HSF and is heated and temperature rising.By heat resource equipment
HSF heating and fluid that temperature rises flows out to high temperature heat source ingress pipe 57 as 100 DEG C of high temperature heat source fluid HP.In height
100 DEG C of the high temperature heat source fluid HP that temperature-heat-source ingress pipe 57 flows is when the flowing of heat source tube 32 in regenerator 30 by weak solution
Sw captures heat, and temperature is reduced to 90 DEG C if reaching high temperature heat source effuser 39.
It is flowed in 90 DEG C of the high temperature heat source fluid HP that high temperature heat source effuser 39 flows in gain of heat fluid effuser 49
50 DEG C of the gain of heat subject fluid TS mixing, become 60 DEG C of fluid-mixing TA and fluid-mixing effuser 59 flow.At this
In embodiment, by by the gain of heat object of the high temperature heat source fluid HP of high temperature heat source effuser 39 and gain of heat fluid effuser 49
Fluid TS mixing, Lai Shixian are flat relative to the flow for being heated fluid and heat source fluid that absorption type heat exchange system 1 passes in and out
Weighing apparatus.Heat utilization equipment HCF is flowed into 60 DEG C of the fluid-mixing TA that fluid-mixing effuser 59 flows, heat is utilized and temperature
It reduces.Fluid-mixing TA after temperature reduces in heat utilization equipment HCF flows out to fluid-mixing with 40 DEG C and flows into pipe 55, with
Afterwards, above-mentioned flowing is repeated.
In absorption type heat exchange system 1 so that temperature relation as described above set up and in fluid-mixing effuser 59
It (is in heat utilization equipment HCF suitable for the temperature that utilizes, in this reality that the temperature of the fluid-mixing TA of flowing, which becomes defined temperature,
Apply in mode as 60 DEG C) mode, determine the flow of gain of heat subject fluid TS flow in gain of heat fluid ingress pipe 51 and in
The ratio between the flow for the medium temperature heat source fluid TP that temperature-heat-source ingress pipe 52 flows.In the present embodiment, make gain of heat subject fluid TS
With the flow-rate ratio substantially 5:2 of medium temperature heat source fluid TP.In addition, increasing if relatively reducing the flow of gain of heat subject fluid TS
The temperature of heat target fluid TS is got higher, if increasing the flow of gain of heat subject fluid TS, the temperature of gain of heat subject fluid TS is lower.
Here, in the gain of heat subject fluid TS of the flowing of gain of heat fluid ingress pipe 51 and the middle temperature-heat-source in the flowing of middle temperature-heat-source ingress pipe 52
The flow-rate ratio of fluid TP can be set in advance in the storage device (not shown) for being set to control device (not shown), can also be with structure
As can be set at any time by being set to the input unit (not shown) of control device.In the present embodiment, by increasing
The aperture of hot fluid valve 51v and medium temperature heat source valve 52v are adjusted to carry out gain of heat subject fluid TS and medium temperature heat source fluid
The adjusting of the flow-rate ratio of TP.The adjusting of the aperture of gain of heat fluid valve 51v and medium temperature heat source valve 52v will be typically based on above-mentioned set
Flow-rate ratio due to control device is simultaneously automatically carried out according to the signal for carrying out self-control device, and however, you can also not by control device
And manually adjust aperture.In addition it is also possible to be led instead of gain of heat fluid valve 51v and medium temperature heat source valve 52v in gain of heat fluid
Enter the interconnecting piece setting triple valve that pipe 51, middle temperature-heat-source ingress pipe 52 and fluid-mixing flow into pipe 55.
If to heating source fluid (high temperature heat source fluid so far illustrating, being entered and left relative to absorption type heat exchange system 1
HP, medium temperature heat source fluid TP) summarized with the flowing for being heated fluid (fluid-mixing TA), then in absorption type heat exchange system
In 1, from heat resource equipment HSF flow out and with 100 DEG C flow into the high temperature heat source fluid HP of absorption type heat exchange system 1 with 30 DEG C from
Absorption type heat exchange system 1 flows out and flows into heat resource equipment HSF, flows out from heat utilization equipment HCF and flows into suction with 40 DEG C
The fluid-mixing TA of receipts formula heat-exchange system 1 is flowed out from absorption type heat exchange system 1 with 60 DEG C and flows into heat utilization equipment
HCF.If the high temperature heat source fluid HP and medium temperature heat source fluid TP that flow into relative to heat resource equipment HSF outflow are considered as heating source
The fluid-mixing TA flowed into relative to heat utilization machine HCF outflow is considered as and is heated fluid, then can be considered as absorption by fluid
Heat-exchange system 1 is in heating source fluid and is heated between fluid and carries out heat exchange action, can be considered as be heated fluid from
Heating source fluid, which has been captured, is cooled to the temperature phase lower than the temperature for being heated fluid with the temperature of the heating source fluid from inflow
The heat-exchange system flowed out after the heat answered.Heating source fluid (the medium temperature heat source fluid flowed out from absorption type heat exchange system 1
TP temperature) is lower, then the heat that heat exchange is carried out in absorption type heat exchange system 1 more increases, and is capable of increasing and is heated stream
The flow of body (fluid-mixing TA).Also, it flows out and flows into heat resource equipment HSF from absorption type heat exchange system 1 making
The flow of temperature-heat-source fluid TP and the high temperature heat source fluid that absorption type heat exchange system 1 is flowed out and flowed into from heat resource equipment HSF
The flow for the fluid-mixing TA that the flow of HP is equal, flows out from absorption type heat exchange system 1 and flows into heat utilization machine HCF with
In the case that the flow for flowing out and flowing into the fluid-mixing TA of absorption type heat exchange system 1 from heat utilization machine HCF is equal, energy
Enough it is considered as heating source fluid and is heated the two fluids of fluid as the independent system divided in absorption type heat exchange system 1
It unites relative to 1 inflow and outflow of absorption type heat exchange system, absorption type heat exchange system 1 is considered as heat exchanger can be brighter
?.As shown in the embodiment, it is suitble to be configured to passing through heat from the medium temperature heat source fluid TP that absorption type heat exchange system 1 flows out
Become high temperature heat source fluid HP after being heated in source device HSF and be back to absorption type heat exchange system 1, is handed over from absorption type heat
The fluid-mixing TA for changing the outflow of system 1 is back to absorption type heat exchange system after being consumed heat by heat utilization machine HCF
1。
In addition, assuming that becoming does not make to flow out the fluid (being heated fluid) flowed into and phase relative to heat utilization equipment HCF
The fluid (heating source fluid) that heat resource equipment HSF outflow flows into is shunted and converged, and standing alone as makes in regenerator 30
In the case that the high temperature heat source fluid HP that heat source tube 32 flows flows to the system of heat source tube 22 of evaporator 20, need to make again
The high temperature heat source fluid HP that the heat source tube 32 of raw device 30 flows over is before flowing into the heat source tube 22 of evaporator 20, and from absorption
The gain of heat subject fluid TS that device 10 and condenser 40 flow out carries out heat exchange to cool down and the heat exchanger of temperature reduction.With this
Relatively, if making to flow out the fluid (being heated fluid) flowed into and opposite as in the present embodiment relative to heat utilization equipment HCF
It shunts and converges in the fluid (heating source fluid) that heat resource equipment HSF outflow flows into, then do not need the above-mentioned hypothesis the case where
The heat exchanger of lower setting, being capable of simplied system structure.Due to the heat exchanger for not needing to be arranged in the case where above-mentioned hypothesis,
So being heated the temperature of fluid caused by can be avoided radiation loss and heat exchange temperature efficiency because carrying out automatic heat-exchanger less than 1
Degree reduces, the reduction of the thermal efficiency caused by can eliminating because of heat exchanger.Also, can also save heat exchanger installation space,
The maintenance test operation of piping, heat exchanger for being passed in and out for fluid relative to heat exchanger.Also, in present embodiment institute
In the absorption type heat exchange system 1 being related to, temperature can be made than the fluid (heating source fluid) that imports from heat resource equipment HSF on one side
Low fluid (being heated fluid) flows out to heat utilization equipment HCF, makes temperature than the fluid that imports from heat utilization equipment HCF on one side
(being heated fluid) low fluid (heating source fluid) flows out to heat resource equipment HSF, can be realized the effective use of heat, can make to inhale
The output of receipts formula heat-exchange system 1 increases.
As described above, according to the present embodiment involved in absorption type heat exchange system 1, can be by the height of importing
Until the temperature of temperature-heat-source fluid HP is cooled to the temperature lower than the fluid-mixing TA of importing, as the middle temperature-heat-source for consuming heat
Fluid TP outflow can make absorption type heat exchange system 1 carry out the heat of heat exchange, i.e. as the thermal output increasing of heat exchanger
Greatly.In addition, due to making in the medium temperature heat source fluid TP of the heating of evaporator 20 from the fluid-mixing TA branch after inflow, and make
Regenerator 30 consumes the high temperature heat source fluid HP of heat and has passed through the gain of heat subject fluid TS of absorber 10 and condenser 40
Converge, so heat exchange can not be carried out by high temperature heat source fluid HP and gain of heat subject fluid TS, be not provided with large-scale heat
Exchanger and simplify apparatus structure, the medium temperature heat source fluid of the temperature lower than the temperature of the fluid-mixing TA of importing can be flowed out
TP.In addition, the discrepancy with the medium temperature heat source fluid TP of the high temperature heat source fluid HP and outflow that flow into absorption type heat exchange system 1
Mouth temperature difference is compared, and the out temperature for reducing the fluid-mixing TA entered and left relative to absorption type heat exchange system 1 is poor, Neng Gouyu
The amount that temperature difference becomes smaller correspondingly increases the flow for the fluid-mixing TA that can be supplied to heat utilization equipment HCF, can expand mixing
The supply range of fluid TA.
Next, being said referring to Fig. 2 to absorption type heat exchange system 2 involved in second embodiment of the present invention
It is bright.Fig. 2 is the schematic system diagram of absorption type heat exchange system 2.Absorption type heat exchange system 2 mainly in point below and absorbs
Formula heat-exchange system 1 (referring to Fig.1) is different.Absorption type heat exchange system 2 is provided with high temperature heat source effuser 39 and middle warm
The high temperature heat source bypass pipe 28 that source ingress pipe 52 is connected.High temperature heat source bypass pipe 28 is to make to flow out from regenerator 30 and in Gao Wenre
Source stream outlet pipe 39 flow high temperature heat source fluid HP a part with flow into evaporator 20 before in middle temperature-heat-source ingress pipe
The pipe that the medium temperature heat source fluid TP of 52 flowings converges, is equivalent to localized heat source bypass of fluid flow path.In high temperature heat source bypass pipe
28 are provided with the high temperature heat source by-passing valve 28v that the flow of the high temperature heat source fluid HP in internal flow is adjusted.Another party
Face is provided in the high temperature heat source effuser 39 than the interconnecting piece downstream with high temperature heat source bypass pipe 28 in internal flow
High temperature heat source fluid HP the high temperature heat source valve 39v that is adjusted of flow.In addition it is also possible to instead of high temperature heat source by-passing valve
28v and high temperature heat source valve 39v and in the interconnecting piece of high temperature heat source effuser 39 and high temperature heat source bypass pipe 28, triple valve is set.
The structure other than the above of absorption type heat exchange system 2 and absorption type heat exchange system 1 (referring to Fig.1) are same.
Effect of the absorption type heat exchange system 2 constituted as described above in addition to absorption type heat exchange system 1 (referring to Fig.1)
Except, also the aperture of high temperature heat source by-passing valve 28v and high temperature heat source valve 39v are adjusted, made from the outflow of regenerator 30
A part of high temperature heat source fluid HP is mixed with the medium temperature heat source fluid TP before flowing into evaporator 20.High temperature heat source by-passing valve
The adjusting of the aperture of 28v and high temperature heat source valve 39v is typically same as absorption type heat exchange system 1, is controlled based on being set in
The flow-rate ratio of device (not shown) is simultaneously automatically carried out according to the signal for carrying out self-control device, and however, you can also not by control device
And manually adjust aperture.It is adjusted by the flow to the high temperature heat source fluid HP mixed with medium temperature heat source fluid TP, energy
It is enough that the temperature and flow of the medium temperature heat source fluid TP flowed in medium temperature fluid effuser 29 are adjusted.In addition, by pair
The flow of the high temperature heat source fluid HP mixed with medium temperature heat source fluid TP is adjusted, to mix to gain of heat subject fluid TS
The flow of high temperature heat source fluid HP be adjusted, can be to the temperature of the fluid-mixing TA flowed in fluid-mixing effuser 59
And flow is adjusted.In the present embodiment, determine the high temperature heat source fluid HP's flowed in high temperature heat source bypass pipe 28
The ratio between the flow of flow and the high temperature heat source fluid HP flowed towards fluid-mixing effuser 59 in high temperature heat source effuser 39, with
Just the temperature of the fluid-mixing TA flowed in fluid-mixing effuser 59 becomes defined temperature.In addition, if relatively increasing
The flow for the high temperature heat source fluid HP that high temperature heat source bypass pipe 28 flows, the then middle temperature-heat-source flowed in medium temperature heat source effuser 29
The temperature of fluid TP rises, and flow increases, and the flow of the high temperature heat source fluid HP mixed with gain of heat subject fluid TS is reduced,
In the temperature decline for the fluid-mixing TA that fluid-mixing effuser 59 flows, flow is reduced.On the other hand, if relatively reducing
The flow for the high temperature heat source fluid HP that high temperature heat source bypass pipe 28 flows, the then middle temperature-heat-source flowed in medium temperature heat source effuser 29
The decline of fluid TP temperature, flow are reduced, and the flow of the high temperature heat source fluid HP mixed with gain of heat subject fluid TS increases,
The temperature for the fluid-mixing TA that fluid-mixing effuser 59 flows rises, and flow increases.In this way, by being bypassed in high temperature heat source
The flow for the high temperature heat source fluid HP that pipe 28 flows is adjusted, can be to the fluid-mixing flowed in fluid-mixing effuser 59
The temperature of medium temperature heat source fluid TP of the temperature of TA with flow and in the flowing of medium temperature heat source effuser 29 is adjusted with flow
Section.
Next, being said referring to Fig. 3 to absorption type heat exchange system 3 involved in third embodiment of the present invention
It is bright.Fig. 3 is the schematic system diagram of absorption type heat exchange system 3.Absorption type heat exchange system 3 mainly in point below and absorbs
Formula heat-exchange system 1 (referring to Fig.1) is different.Absorption type heat exchange system 3 become to independent two heat utilization equipment HCF1,
The system of HCF2 supply fluid.For absorption type heat exchange system 3, high temperature heat source effuser 39 is not flowed out with gain of heat fluid
Pipe 49 connects, not set fluid-mixing effuser 59 (referring to Fig.1).It is configured to gain of heat fluid effuser 49 and heat utilization equipment
HCF1 connection, will be absorbed device 10 and the heated gain of heat subject fluid TS of condenser 40 is supplied to heat utilization equipment HCF1.
One end that heat loss finishes fluid hose 56 is connected in heat utilization equipment HCF1.It is to constitute heat supply quilt that heat loss, which finishes fluid hose 56,
Heat utilization equipment HCF1 is consumed and the pipe of the flow path for the gain of heat subject fluid TS flowing that temperature reduces.Heat loss finishes fluid hose
Fluid hose 53 after 56 other end is connected with middle temperature-heat-source ingress pipe 52 and shunts.Fluid hose 53 is constituted for shunting after shunting
The pipe of the flow path of fluid TL flowing.Shunting fluid TL is removed from the gain of heat subject fluid TS for finishing the flowing of fluid hose 56 in heat loss
Remove to branch to remaining fluid after the medium temperature heat source fluid TP of middle temperature-heat-source ingress pipe 52.Fluid hose 53 is provided with after shunting
Fluid valve 53v after the shunting that the flow of fluid in internal flow is adjusted.It is not provided with gain of heat fluid valve 51v (reference
Fig. 1).The other end of fluid hose 53 and gain of heat fluid ingress pipe 51 and heat loss finish the respective end of fluid hose 54 after shunting
Connection.High temperature heat source effuser 39 is configured to connect with heat utilization equipment HCF2, the high temperature heat source stream that will be flowed out from regenerator 30
Body HP is supplied to heat utilization equipment HCF2.One end that heat loss finishes fluid hose 54 is connected in heat utilization equipment HCF2.Heat disappears
It is to constitute heat supply by heat utilization equipment HCF2 consumption and gain of heat subject fluid TS that temperature reduces flows that consumption, which finishes fluid hose 54,
Flow path pipe.Heat loss finishes the other end and gain of heat fluid ingress pipe 51 and fluid hose 53 is respective after shunting of fluid hose 54
End connection.In absorption type heat exchange system 3, after shunting fluid hose 53 flow shunting fluid TL with it is complete in heat loss
Finish the mixed gain of heat subject fluid TS of high temperature heat source fluid HP that fluid hose 54 flows to flow in gain of heat fluid ingress pipe 51.It inhales
The structure other than the above of receipts formula heat-exchange system 3 and absorption type heat exchange system 1 (referring to Fig.1) are same.
It, can be to independent heat utilization equipment HCF1,2 points in the absorption type heat exchange system 3 constituted as described above
It Gong Gei not heat.It is absorbed device 10 and the heated gain of heat subject fluid TS of condenser 40 is supplied to heat utilization equipment HCF1,
Heat is utilized after temperature reduction by heat utilization equipment HCF1, flows out to heat loss and finishes fluid hose 56.On the other hand, from regeneration
The high temperature heat source fluid HP that device 30 flows out is supplied to heat utilization equipment HCF2, is utilized and temperature drop in heat by heat utilization equipment HCF2
After low, flow out to heat loss and finish fluid hose 54.The increasing that heat loss finishes fluid hose 56 is flowed out to from heat utilization equipment HCF1
Heat target fluid TS is split into the medium temperature heat source fluid TP of middle temperature-heat-source ingress pipe 52 flowing and fluid hose 53 flows after shunting
Dynamic shunting fluid TL.Evaporator 20 is being flowed into refrigerant in the medium temperature heat source fluid TP of middle temperature-heat-source ingress pipe 52 flowing
Liquid Vf is heated after own temperature reduction, flows into heat resource equipment HSF via medium temperature heat source effuser 29.Another party
Face, the shunting fluid TL and flowed out from heat utilization equipment HCF2 and finish fluid hose in heat loss that fluid hose 53 flows after shunting
The high temperature heat source fluid HP of 54 flowings merges as gain of heat subject fluid TS.Gain of heat subject fluid TS is imported via gain of heat fluid
Pipe 51 flows into absorber 10 and is heated.In absorption type heat exchange system 3, flowed after centering temperature-heat-source valve 52v and shunting
The aperture of body valve 53v is adjusted such that the gain of heat subject fluid TS flowed in gain of heat fluid effuser 49 becomes defined temperature
Degree.It is sharp from heat in the temperature ratio of the gain of heat subject fluid TS flowed out from heat utilization equipment HCF1 in absorption type heat exchange system 3
With equipment HCF2 outflow high temperature heat source fluid HP temperature it is low in the case where, flow into the medium temperature heat source fluid TP of evaporator 20
Temperature it is low and suitable.So, it can be utilized respectively from regenerator 30 and flow in different heat utilization equipment HCF2, HCF1
High temperature heat source fluid HP out and it is absorbed device 10 and heated gain of heat subject fluid TS the two fluids of condenser 40.It can
So that the heat utilization equipment HCF2 for importing high temperature heat source fluid HP is compared the purposes of high temperature, imports the heat benefit of gain of heat subject fluid TS
It is the purposes for comparing low temperature with equipment HCF1.
Next, being said referring to Fig. 4 to absorption type heat exchange system 4 involved in the 4th embodiment of the invention
It is bright.Fig. 4 is the schematic system diagram of absorption type heat exchange system 4.Absorption type heat exchange system 4 mainly in point below and absorbs
Formula heat-exchange system 2 (referring to Fig. 2) is different.Absorption type heat exchange system 4 is configured to flow into from high temperature heat source effuser 39 supreme
The not direct middle temperature-heat-source in the flowing of middle temperature-heat-source ingress pipe 52 of a part of high temperature heat source fluid HP of temperature-heat-source bypass pipe 28
Fluid TP converges, and utilizes and with heat utilization equipment HCFA is added in heat in middle temperature-heat-source ingress pipe 52 stream after temperature reduction
Dynamic medium temperature heat source fluid TP converges.In absorption type heat exchange system 4, high temperature heat source bypass pipe 28 is divided into than additional heat benefit
With equipment HCFA high temperature heat source bypass pipe 28A on the upstream side and than the high temperature heat source of additional heat utilization equipment HCFA downstream
Bypass pipe 28B.The structure other than the above and absorption type heat exchange system 2 (referring to Fig. 2) of absorption type heat exchange system 4 are same.
Since the absorption type heat exchange system 4 that constitutes in this way can supply heat to multiple heat utilization equipment HCF, HCFA, usually with absorption
The case where formula heat-exchange system 2 (referring to Fig. 2), is compared, and the temperature of the high temperature heat source fluid HP of middle temperature-heat-source ingress pipe 52 is flowed into
It is lower, the temperature of the medium temperature heat source fluid TP flowed out from evaporator 20 is also lower, so being able to carry out more heat exchanges.And
And in the temperature of the high temperature heat source fluid HP flowed out from additional heat utilization equipment HCFA than the increasing flowed out from heat utilization equipment HCF
In the case that the temperature of heat target fluid TS is low, compared with absorption type heat exchange system 1 (referring to Fig.1), it can reduce and flow into
The temperature of the medium temperature heat source fluid TP of evaporator 20, can promote heat utilization and is applicable in.
Next, being said referring to Fig. 5 to absorption type heat exchange system 5 involved in the 5th embodiment of the invention
It is bright.Fig. 5 is the schematic system diagram of absorption type heat exchange system 5.Absorption type heat exchange system 5 mainly in point below and absorbs
Formula heat-exchange system 1 (referring to Fig.1) is different.Absorption type heat exchange system 5 becomes with heat utilization equipment HCF independently to additional heat
Utilize the system of equipment HCFA supply fluid.Absorption type heat exchange system 5, which is provided with, to be flowed in high temperature heat source effuser 39
A part of high temperature heat source fluid HP is guided to the addition heat source ingress pipe 58A of additional heat utilization equipment HCFA.In additional heat source
Ingress pipe 58A is provided with the addition heat source valve 58v that the flow of the fluid in internal flow is adjusted.Than with additional heat source
The high temperature heat source effuser 39 of the interconnecting piece downstream of ingress pipe 58A is provided with the flow progress to the fluid in internal flow
The high temperature heat source valve 39v of adjusting.One end of additional heat source effuser 58B, the addition are connected in additional heat utilization equipment HCFA
Heat source effuser 58B heat supply is added that heat utilization equipment HCFA is utilized and high temperature heat source fluid HP that temperature reduces flows.It chases after
The other end of heating source effuser 58B is connect with the gain of heat fluid ingress pipe 51 than gain of heat fluid valve 51v downstream, is configured to
The gain of heat object for making the high temperature heat source fluid HP flowed out from additional heat utilization equipment HCFA and being flowed in gain of heat fluid ingress pipe 51
Fluid TS converges.The structure other than the above of absorption type heat exchange system 5 and absorption type heat exchange system 1 (referring to Fig.1) are same.
The absorption type heat exchange system 5 constituted in this way can supply heat to multiple heat utilization equipment HCF, HCFA.In addition, from heat utilization
The temperature of the fluid-mixing TA of equipment HCF outflow is than the temperature of the high temperature heat source fluid HP flowed out from additional heat utilization equipment HCFA
In the case where low, the temperature for flowing into the medium temperature heat source fluid TP of evaporator 20 can be very low, can promote heat utilization and it is preferred that.It can
The heat utilization equipment HCFA for importing high temperature heat source fluid HP is set to compare the purposes of high temperature, the heat utilization for importing fluid-mixing TA is set
Standby HCF is the purposes for comparing low temperature.
In the above description, gain of heat subject fluid TS is from absorber 10 to 40 serial flow of condenser, but can also be from
Condenser 40 can also flow side by side to 10 serial flow of absorber to absorber 10 and condenser 40.
In the above description, due to heating source fluid (high temperature heat source fluid HP, medium temperature heat source fluid TP) be heated
Fluid (fluid-mixing TA, gain of heat subject fluid TS) is shunted and is converged, so being fluid of the same race.Applied fluid removes
Except warm water, it is also possible to heat agent liquid, chemical liquid.Especially according to the boiling point heating agent liquid higher than water,
Chemical liquid then will not make high pressure act on fluid, can apply supreme temperature field to inhibit the boiling of fluid.
Claims (10)
1. a kind of absorption type heat exchange system, which is characterized in that have:
Condensation part, the condensation heat that discharges when becoming refrigerant liquid by the condensation of the steam of refrigerant make the temperature for being heated fluid
Degree rises；
Evaporation part imports above-mentioned refrigerant liquid from above-mentioned condensation part, by capture from the first heating source fluid imported it is above-mentioned
Refrigerant liquid evaporates and becomes evaporation latent heat required when refrigerant vapour, drop the temperature of above-mentioned first heating source fluid
It is low；
Absorption portion imports above-mentioned refrigerant vapour from above-mentioned evaporation part, and the above-mentioned refrigerant imported is absorbed by absorbing liquid and is steamed
Vapour and absorption heat that while becoming the weak solution that concentration reduces discharges rises to make to be heated the temperature of fluid；And
Reproducing unit imports above-mentioned weak solution from above-mentioned absorption portion, by from the second heating source fluid capture heating imported it is upper
State weak solution make refrigerant from above-mentioned weak solution be detached from and become the concentrated solution that rises of concentration needed for heat, to make above-mentioned second
The temperature of heating source fluid reduces,
Above-mentioned absorption type heat exchange system is configured to recycle by the sorption type heat pump of above-mentioned absorbing liquid and above-mentioned refrigerant, above-mentioned suction
Receipts portion pressure and temperature internal compared with above-mentioned reproducing unit are low, above-mentioned evaporation part pressure internal compared with above-mentioned condensation part
And temperature is low,
And be configured to by from be fed to before above-mentioned condensation part and above-mentioned absorption portion it is above-mentioned be heated fluid branch after
The above-mentioned of a part is heated fluid as above-mentioned first heating source fluid and is directed into above-mentioned evaporation part.
2. absorption type heat exchange system according to claim 1, which is characterized in that
Above-mentioned absorption type heat exchange system is configured at least one of the above-mentioned second heating source fluid flowed out from above-mentioned reproducing unit
Divide and is mixed with the above-mentioned fluid that is heated flowed out from at least one party in above-mentioned condensation part and above-mentioned absorption portion.
3. absorption type heat exchange system according to claim 2, which is characterized in that
Above-mentioned absorption type heat exchange system is configured to the above-mentioned quilt that setting flows into above-mentioned condensation part and above-mentioned absorption portion
It heats the flow of fluid and flows into the above-mentioned stream for being heated fluid of above-mentioned evaporation part as above-mentioned first heating source fluid
The ratio between amount so that at least part of the above-mentioned second heating source fluid flowed out from above-mentioned reproducing unit with from above-mentioned condensation part and
The above-mentioned mixed temperature for being heated fluid that mixes of fluid that is heated of at least one party's outflow in above-mentioned absorption portion is as regulation
Temperature.
4. absorption type heat exchange system according to claim 2 or 3, which is characterized in that
Above-mentioned absorption type heat exchange system be configured to flowed out from at least one party in above-mentioned condensation part and above-mentioned absorption portion it is upper
State be heated fluid mixing before a part from above-mentioned second heating source fluid branch above-mentioned second heating source fluid and
Remaining above-mentioned second heating source fluid after above-mentioned branch is flowed with from at least one party in above-mentioned condensation part and above-mentioned absorption portion
The above-mentioned mixed fluid of fluid that is heated out flows out with being individually separated from above-mentioned absorption type heat exchange system.
5. absorption type heat exchange system described in any one of claim 1 to 3, which is characterized in that
Above-mentioned absorption type heat exchange system has localized heat source bypass of fluid flow path, which makes
By the above-mentioned second heating source fluid branch flowed out from above-mentioned reproducing unit a part above-mentioned second heating source fluid with led
The above-mentioned first heating source fluid entered to before above-mentioned evaporation part converges.
6. absorption type heat exchange system according to claim 5, which is characterized in that
Above-mentioned absorption type heat exchange system is configured to set the above-mentioned second heating source fluid flowed out from above-mentioned reproducing unit
The flow of above-mentioned localized heat source bypass of fluid flow path is not flowed into and in above-mentioned localized heat source bypass of fluid flow path
The ratio between flow so that from above-mentioned reproducing unit flow out above-mentioned second heating source fluid at least part with from above-mentioned condensation part with
And the above-mentioned mixed temperature for being heated fluid that mixes of fluid that is heated of at least one party's outflow in above-mentioned absorption portion is as rule
Fixed temperature.
7. absorption type heat exchange system according to claim 5, which is characterized in that
Above-mentioned absorption type heat exchange system is configured to make to add above-mentioned the second of above-mentioned localized heat source bypass of fluid flow path
Heat source fluid by heat utilization and temperature reduce after with the above-mentioned first heating source fluid before being fed to above-mentioned evaporation part
Converge.
8. absorption type heat exchange system according to claim 2 or 3, which is characterized in that
Above-mentioned absorption type heat exchange system be configured to flowed out from at least one party in above-mentioned condensation part and above-mentioned absorption portion it is upper
State be heated fluid mixing before a part from above-mentioned second heating source fluid branch above-mentioned second heating source fluid and
Remaining above-mentioned second heating source fluid after above-mentioned branch is flowed with from at least one party in above-mentioned condensation part and above-mentioned absorption portion
The above-mentioned mixed fluid of fluid that is heated out flows out with being individually separated from above-mentioned absorption type heat exchange system,
Above-mentioned absorption type heat exchange system has localized heat source bypass of fluid flow path, which makes
By the above-mentioned second heating source fluid branch flowed out from above-mentioned reproducing unit a part above-mentioned second heating source fluid with led
The above-mentioned first heating source fluid entered to before above-mentioned evaporation part converges.
9. absorption type heat exchange system according to claim 8, which is characterized in that
Above-mentioned absorption type heat exchange system is configured to make to add above-mentioned the second of above-mentioned localized heat source bypass of fluid flow path
Heat source fluid by heat utilization and temperature reduce after with the above-mentioned first heating source fluid before being fed to above-mentioned evaporation part
Converge.
10. absorption type heat exchange system according to claim 1, which is characterized in that
Above-mentioned absorption type heat exchange system is configured at least one of the above-mentioned second heating source fluid flowed out from above-mentioned reproducing unit
Point with flowed out from above-mentioned condensation part it is above-mentioned be heated fluid be individually separated from above-mentioned absorption type heat exchange system outflow.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017158910A JP6896968B2 (en) | 2017-08-21 | 2017-08-21 | Absorption heat exchange system |
| JP2017-158910 | 2017-08-21 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN109425143A true CN109425143A (en) | 2019-03-05 |
Family
ID=65514469
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821279725.9U Active CN208817757U (en) | 2017-08-21 | 2018-08-09 | Absorption type heat exchange system |
| CN201810902236.2A Pending CN109425143A (en) | 2017-08-21 | 2018-08-09 | Absorption type heat exchange system |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821279725.9U Active CN208817757U (en) | 2017-08-21 | 2018-08-09 | Absorption type heat exchange system |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6896968B2 (en) |
| CN (2) | CN208817757U (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2020140444A (en) | 2019-02-28 | 2020-09-03 | セイコーエプソン株式会社 | Maintenance support system and terminal used for the same |
| CN113531704B (en) * | 2021-07-06 | 2022-07-12 | 北京建筑大学 | Low-temperature area heat and cold supply system and operation method |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1877223A (en) * | 2005-06-09 | 2006-12-13 | 三洋电机株式会社 | Operation method of single or dual uses adsorption type freezing machine |
| CN101629733A (en) * | 2009-08-18 | 2010-01-20 | 清华大学 | Method for reducing return water temperature of heat supply pipeline |
| CN203704109U (en) * | 2014-02-28 | 2014-07-09 | 烟台荏原空调设备有限公司 | Absorption type heat exchange unit |
| CN104832970A (en) * | 2015-04-24 | 2015-08-12 | 珠海格力电器股份有限公司 | Absorption-type heat exchanger unit |
| CN104848331A (en) * | 2015-04-24 | 2015-08-19 | 珠海格力电器股份有限公司 | Heat supplying system |
| CN104949378A (en) * | 2014-03-25 | 2015-09-30 | 荏原冷热系统株式会社 | Absorption heat pump |
| KR20160010805A (en) * | 2014-07-18 | 2016-01-28 | 주식회사 성지테크 | Free cooling system with absorption chiller |
-
2017
- 2017-08-21 JP JP2017158910A patent/JP6896968B2/en active Active
-
2018
- 2018-08-09 CN CN201821279725.9U patent/CN208817757U/en active Active
- 2018-08-09 CN CN201810902236.2A patent/CN109425143A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1877223A (en) * | 2005-06-09 | 2006-12-13 | 三洋电机株式会社 | Operation method of single or dual uses adsorption type freezing machine |
| CN101629733A (en) * | 2009-08-18 | 2010-01-20 | 清华大学 | Method for reducing return water temperature of heat supply pipeline |
| CN203704109U (en) * | 2014-02-28 | 2014-07-09 | 烟台荏原空调设备有限公司 | Absorption type heat exchange unit |
| CN104949378A (en) * | 2014-03-25 | 2015-09-30 | 荏原冷热系统株式会社 | Absorption heat pump |
| KR20160010805A (en) * | 2014-07-18 | 2016-01-28 | 주식회사 성지테크 | Free cooling system with absorption chiller |
| CN104832970A (en) * | 2015-04-24 | 2015-08-12 | 珠海格力电器股份有限公司 | Absorption-type heat exchanger unit |
| CN104848331A (en) * | 2015-04-24 | 2015-08-19 | 珠海格力电器股份有限公司 | Heat supplying system |
Non-Patent Citations (1)
| Title |
|---|
| 徐邦裕，陆亚俊: "《热泵》", 31 July 1988, 中国建筑工业出版社 * |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6896968B2 (en) | 2021-06-30 |
| CN208817757U (en) | 2019-05-03 |
| JP2019035561A (en) | 2019-03-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4475361A (en) | Multi-effect heat-pump for heating and cooling | |
| CN208817757U (en) | Absorption type heat exchange system | |
| JPH06507965A (en) | Regenerative absorption cycle with multi-stage breathing apparatus | |
| CN102287950B (en) | Absorbing heat pump | |
| CN209263411U (en) | Absorption type heat exchange system | |
| JP2006138614A (en) | Absorbing type heat pump | |
| CN207407544U (en) | Two segment type lithium bromide adsorption water chilling unit of hot water and steam economic benefits and social benefits | |
| CN108180670A (en) | Absorption type heat exchange system | |
| CN208817758U (en) | Absorption type heat exchange system | |
| CN104180555A (en) | Cool double-effect lithium bromide spray absorption type refrigeration cycle system | |
| CN209431705U (en) | Absorption type heat exchange system | |
| CN207662009U (en) | Absorption type heat exchange system | |
| CN209085115U (en) | Absorption type heat exchange system | |
| CN209246459U (en) | Absorption type heat exchange system | |
| CN208154873U (en) | The solution series type lithium bromide absorption type refrigeration heat pump unit of variable effect | |
| CN208154867U (en) | The solution lithium bromide absorption type refrigeration heat pump of the falling tandem type unit of variable effect | |
| CN208154868U (en) | The solution parallel connection type lithium bromide absorption type refrigeration heat pump unit of variable effect | |
| CN100567853C (en) | A kind of backheating type sodium rhodanate-ammonia absorption heat pump system | |
| CN101699195B (en) | Smoke hot water type lithium bromide absorbing cold water or cold-hot water set with booster pump | |
| JP4376788B2 (en) | Absorption refrigerator | |
| KR100877024B1 (en) | Apparatus for supplying warm water during cooling mode in absorption water cooler and heater | |
| CN108426388A (en) | Absorption power and spray type refrigerating combined cycle system and its working method | |
| CN106352590A (en) | Combined heating and power system | |
| CN106440468A (en) | Combined heating and power system | |
| CN108645071A (en) | The solution lithium bromide absorption type refrigeration heat pump of the falling tandem type unit of variable effect |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |