CN106642831A - Composite heat exchanger for organic Rankine cycle power generating system - Google Patents
Composite heat exchanger for organic Rankine cycle power generating system Download PDFInfo
- Publication number
- CN106642831A CN106642831A CN201611267451.7A CN201611267451A CN106642831A CN 106642831 A CN106642831 A CN 106642831A CN 201611267451 A CN201611267451 A CN 201611267451A CN 106642831 A CN106642831 A CN 106642831A
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- Prior art keywords
- area
- gas
- liquid
- heat area
- sensible heat
- 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.)
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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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/022—Evaporators with plate-like or laminated elements
-
- 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
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/02—Details of evaporators
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/043—Condensers made by assembling plate-like or laminated elements
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses a composite heat exchanger for an organic Rankine cycle power generating system. The composite heat exchanger comprises a liquid-phase sensible heat area, a gas-liquid latent heat area and a gas-phase sensible heat area, wherein the cross section area of the liquid-phase sensible heat area, the gas-liquid latent heat area and the gas-phase sensible heat area is different. The composite heat exchanger has the advantages that the liquid-phase sensible heat area, the gas-liquid latent heat area and the gas-phase sensible heat area are separated, optical cross section area of the liquid-phase sensible heat area, the gas-liquid latent heat area and the gas-phase sensible heat area is achieved, certain flow speed is maintained, the heat exchanger is reliable and small in size, the efficiency of the organic Rankine cycle power generating system is improved to the maximum extent, and equipment cost is reduced.
Description
Technical field
The present invention relates to a kind of organic Rankine cycle power generation system composite heat exchanger, belongs to plant equipment technology neck
Domain.
Background technology
As shown in figure 1, organic Rankine cycle power generation system is by working medium pump, evaporimeter, turbine-generator, condenser, reception
Container etc. is constituted.Operation principle is as follows：First the liquid phase organic working medium of high pressure compressed is conveyed to into evaporimeter by working medium pump, is conveyed
High pressure liquid in evaporimeter communicates the heating evaporation of pervaporation device thermal source becomes gases at high pressure.Subsequently, gases at high pressure are by saturating
The turbine expansion of flat-generator is low temperature, the gas of low pressure, and provides power to turbine, and it is enterprising that its power is transmitted to generator
Row generates electricity.Low temperature is become by the expansion process of turbine, the working fluid of low pressure is fed in condenser, subsequently by cooling water
Cooling condensation become and gather after liquid reception tank.Gather the liquid condition working fluid received in tank and begin through work again
The operation of the pump of dynamic fluid starts, and is fed to the cycle operation process of evaporimeter.
But, when low-temperature heat source is made full use of, low-temperature heat source is utilized in organic Rankine cycle power generation system and generated electricity
It is not fully developed before, can only obtain the problem of the more inefficient limit, and then because of it in the capital cost of the equal amount of money
With relatively low efficiency, the longer problem of investment cycle can be faced, in order to overcome this problem, it is necessary to change to greatest extent
Kind efficiency simultaneously reduces cost of equipment.
To solve the above problems, organic Rankine cycle power generation system can adopt compact heat exchanger, especially by should
With plate-fin heat exchanger, traditional plate-fin heat exchanger type heat exchanger structure as shown in Figures 2 and 3 is come schematically illustrate.
The special construction of the fin of plate-fin heat exchanger, makes fluid form great turbulence level, so as to effectively reduce thermal resistance, improves
Heat transfer efficiency.Heat transfer efficiency is relatively low with power dissipation ratio, is accurately controlled medium temperature.
But if evaporimeter and condenser are run into, and fluid phase state change will occur, hand over there is heat in same phase state
The heat exchanger for changing is different, can run into 3 kinds of not homophase state changes, including liquid, gas and liquid, gas boundary state.Such as,
By evaporimeter as an example for, it is interval to there will be liquid phase sensible heat in same heat exchanger, from liquid to gaseous latent heat
Interval, and gaseous sensible heat interval.
Plate-fin heat exchanger as shown in Figures 2 and 3, including liquid phase sensible heat area, gas-liquid latent heat area and gas phase sensible heat area, it is right
For fluid of the same race, when contrasting the plate-fin heat exchanger and evaporimeter or condenser with iso-cross-section, plate-fin heat exchanger meeting
Facing will ensure that all intervals obtain the problem being difficult to during optimal heat transfer effect.Even same flow of fluid medium
It is dynamic, because the density variation of great disparity between liquid phase and gaseous state causes the flow velocity in same runner to there is significant difference, additionally include
Evaporation Phenomenon is different in interior 3 kinds different physical state intervals physical propertys, heat conduction properties, if with one of which phase work
When designing optimal cross-section for reference object, other two kinds of phases inherently off-target cross-sectional extent, single cross section
Method for designing can reduce heat exchanger effectiveness, meanwhile, select any as also difficult during suitable reference object.
The content of the invention
The technical problem to be solved in the present invention is not enough for more than, there is provided a kind of organic Rankine cycle power generation system is with again
Heat exchanger is closed, with liquid phase sensible heat region, latent heat region and gas phase sensible heat region are separated, each interval cross section is made
Reach most preferably, maintain certain flow velocity, make heat exchanger more reliable, the small volume of heat exchanger changes to greatest extent
It has been apt to the efficiency of organic Rankine cycle power generation system and has reduced the advantage of cost of equipment.
To solve above technical problem, the present invention is employed the following technical solutions：
A kind of organic Rankine cycle power generation system composite heat exchanger, including liquid phase sensible heat area, gas-liquid latent heat area and gas phase be aobvious
Hot-zone, the cross-sectional area in the liquid phase sensible heat area, gas-liquid latent heat area and gas phase sensible heat area is different.
Further, the liquid phase sensible heat area is located at the bottom of heat exchanger, and liquid phase sensible heat area is annular, liquid phase sensible heat area
It is that the flow media of undergoing phase transition occurs heat exchange by liquid phase state.
Further, the gas-liquid latent heat area is arranged parallel with liquid phase sensible heat area, and the annular inboard in liquid phase sensible heat area is surrounded
Space is gas-liquid latent heat area, and gas-liquid latent heat area connects with liquid phase sensible heat area.
Further, the gas-liquid latent heat area compares liquid phase sensible heat area with bigger cross-sectional area, gas-liquid latent heat area
Flow media flow direction it is contrary with liquid phase sensible heat area.
Further, the gas phase sensible heat area is arranged on liquid phase sensible heat area and gas-liquid latent heat area top, gas phase sensible heat position
In the top of heat exchanger, gas phase sensible heat area connects with gas-liquid latent heat area.
Further, the gas phase sensible heat area compares gas-liquid latent heat area with bigger cross-sectional area, gas phase sensible heat area
It is that the flow media of undergoing phase transition occurs heat exchange by gas phase state.
Further, using the whole of the thermal source structure composition heat exchange alternately laminated with flow media in the heat exchanger
Body structure.
Heat exchanger of the present invention has advantages below：
Heat exchanger of the present invention is separated in liquid phase sensible heat region, latent heat region and gas phase sensible heat region, adjustment
Each interval cross section, maintains certain flow velocity, makes heat exchanger more reliable, and it is compact that each interval is done, heat exchanger
Small volume, improves to greatest extent the efficiency of organic Rankine cycle power generation system and reduces cost of equipment.
With reference to the accompanying drawings and examples the present invention is described in detail.
Description of the drawings
Accompanying drawing 1 is the structural representation of organic Rankine cycle power generation system in background of invention；
Accompanying drawing 2 is the signal that evaporimeter thermal source end section is illustrated in traditional plate-fin heat exchanger in background of invention
Figure；
Accompanying drawing 3 is the schematic diagram of the flow media end section of evaporimeter in traditional plate-fin heat exchanger in background of invention；
Accompanying drawing 4 is the schematic diagram of the thermal source end section of evaporimeter in plate-fin heat exchanger in the embodiment of the present invention；
Accompanying drawing 5 is the schematic diagram of the flow media end section of evaporimeter in plate-fin heat exchanger in the embodiment of the present invention；
Accompanying drawing 6 be improve in the embodiment of the present invention after in plate-fin heat exchanger the flow media end section of evaporimeter schematic diagram；
In figure,
1- liquid phase sensible heats area, 2- gas-liquid latent heat area, 3- gas phase sensible heats area, 4- separation layers.
Specific embodiment
Embodiment 1, as shown in Figure 4, Figure 5, a kind of organic Rankine cycle power generation system composite heat exchanger, including liquid phase
Sensible heat area 1, gas-liquid latent heat area 2 and gas phase sensible heat area 3.
The liquid phase sensible heat area 1 is located at the bottom of heat exchanger, and liquid phase sensible heat area 1 is annular, and liquid phase sensible heat area 1 is that occur
There is heat exchange by liquid phase state in the flow media of phase change.
The gas-liquid latent heat area 2 is arranged parallel with liquid phase sensible heat area 1, and the annular inboard encircling space in liquid phase sensible heat area 1 is
Gas-liquid latent heat area 2, gas-liquid latent heat area 2 connects with liquid phase sensible heat area 1, and gas-liquid latent heat area 2 compares liquid phase sensible heat area 1 to be had more
Big cross-sectional area, the flow direction of the flow media in gas-liquid latent heat area 2 is contrary with liquid phase sensible heat area 1.
The gas phase sensible heat area 3 is arranged on liquid phase sensible heat area 1 and the top of gas-liquid latent heat area 2, and gas phase sensible heat area 3 is located at heat friendship
The top of parallel operation, gas phase sensible heat area 3 connects with gas-liquid latent heat area 2, and gas phase sensible heat area 3 compares gas-liquid latent heat area 2 with bigger
Cross-sectional area, gas phase sensible heat area 3 is that the flow media of undergoing phase transition occurs heat exchange by gas phase state.
Embodiment 2, as shown in Fig. 4, Fig. 5, Fig. 6, a kind of organic Rankine cycle power generation system composite heat exchanger, including
Liquid phase sensible heat area 1, gas-liquid latent heat area 2 and gas phase sensible heat area 3.
The liquid phase sensible heat area 1 is located at the bottom of heat exchanger, and liquid phase sensible heat area 1 is annular, and liquid phase sensible heat area 1 is that occur
There is heat exchange by liquid phase state in the flow media of phase change.
The gas-liquid latent heat area 2 is arranged parallel with liquid phase sensible heat area 1, and the annular inboard encircling space in liquid phase sensible heat area 1 is
Gas-liquid latent heat area 2, gas-liquid latent heat area 2 connects with liquid phase sensible heat area 1, and gas-liquid latent heat area 2 compares liquid phase sensible heat area 1 to be had more
Big cross-sectional area, the flow direction of the flow media in gas-liquid latent heat area 2 is contrary with liquid phase sensible heat area 1.
Separation layer 4 is provided between the gas-liquid latent heat area 2 and liquid phase sensible heat area 1, separation layer 4 maintains vacuum state, every
Absciss layer 4 can to greatest extent reduce the heat exchange between gas-liquid latent heat area 2 and liquid phase sensible heat area 1.
The separation layer 4 is annular, and separation layer 4 is applied between gas-liquid latent heat area 2 and liquid phase sensible heat area 1, separation layer
The 4 patch liquid phase sensible heat of side wall 41 area 1 is arranged, and the shape of side wall 41 of separation layer 4 is identical with 1 inner wall shape of liquid phase sensible heat area,
The patch gas-liquid latent heat of opposite side wall 42 area 2 of separation layer 4 is arranged, the shape of side wall 42 and the outer wall shape of gas-liquid latent heat area 2 of separation layer 4
Shape is identical.
The configuration of the separation layer 4 causes heat exchanger to reduce the heat leakage between each interval, and heat loss is dropped to most
It is low, the efficiency of the heat exchange that improve
The gas phase sensible heat area 3 is arranged on liquid phase sensible heat area 1 and the top of gas-liquid latent heat area 2, and gas phase sensible heat area 3 is located at heat exchanger
Top, gas phase sensible heat area 3 connects with gas-liquid latent heat area 2, gas phase sensible heat area 3 compare gas-liquid latent heat area 2 have it is bigger transversal
Face area, gas phase sensible heat area 3 is that the flow media of undergoing phase transition occurs heat exchange by gas phase state.
Tied with the overall of the alternately laminated structure composition heat exchange of flow media using thermal source in the heat exchanger of the present invention
Structure.
As illustrated as case by evaporimeter in Fig. 4 and Fig. 5, the flow media that plan is evaporated is with liquid phase from liquid phase
The top in sensible heat area flows to its bottom and carries out heat exchange, and the liquid phase sent from liquid phase sensible heat area is evaporated to gas after flowing into from liquid phase
The gas-liquid latent heat area on top is flowed to after state, from the flow media of gas-liquid latent heat area supply the gas phase sensible heat area of superheated steam is become
Domain, compares shown in Fig. 3 interval more compact so as to constitute, and each interval characteristic can be preferably maintained again, has accomplished effective differentiation
Configuration.
In accompanying drawing, the in/out mouth end of each fluid is indicated respectively on drawing with dotted line.It is attached when illustrating,
It is displayed as being not limited thereto in left and right object formula but practical application, also this structure may be constituted by left side or right side.
Compared with evaporimeter, flow direction is with the contrary same or like composition of morphosis for condenser.Carry out cold
Solidifying object is interval in the liquid phase sensible heat that liquid phase state carries out heat exchange, and flow media is condensed into after liquid phase with liquid from gaseous state
Phase state flows out to bottom and is fed to gas-liquid latent heat area, and the flow media of superheated steam state is converted to into saturated-vapor state
After be fed to gas phase sensible heat region.
The above for best mode for carrying out the invention citing, wherein to be this area common for the part do not addressed in detail
The common knowledge of technical staff.Protection scope of the present invention is defined by the content of claim, any technology based on the present invention
The equivalent transformation for enlightening and carrying out, also within protection scope of the present invention.
Claims (7)
1. a kind of organic Rankine cycle power generation system composite heat exchanger, including liquid phase sensible heat area（1）, gas-liquid latent heat area（2）
And gas phase sensible heat area（3）, it is characterised in that：The liquid phase sensible heat area（1）, gas-liquid latent heat area（2）And gas phase sensible heat area（3）Horizontal stroke
Area of section is different.
2. a kind of organic Rankine cycle power generation system composite heat exchanger as claimed in claim 1, it is characterised in that：It is described
Liquid phase sensible heat area（1）It is located at the bottom of heat exchanger, liquid phase sensible heat area（1）For annular, liquid phase sensible heat area（1）It is undergoing phase transition
Flow media there is heat exchange by liquid phase state.
3. a kind of organic Rankine cycle power generation system composite heat exchanger as claimed in claim 1, it is characterised in that：It is described
Gas-liquid latent heat area（2）With liquid phase sensible heat area（1）It is parallel to arrange, liquid phase sensible heat area（1）Annular inboard encircling space it is latent for gas-liquid
Hot-zone（2）, gas-liquid latent heat area（2）With liquid phase sensible heat area（1）It is connection.
4. a kind of organic Rankine cycle power generation system composite heat exchanger as claimed in claim 1, it is characterised in that：It is described
Gas-liquid latent heat area（2）Compare liquid phase sensible heat area（1）With bigger cross-sectional area, gas-liquid latent heat area（2）Flow media
Flow direction and liquid phase sensible heat area（1）On the contrary.
5. a kind of organic Rankine cycle power generation system composite heat exchanger as claimed in claim 1, it is characterised in that：It is described
Gas phase sensible heat area（3）It is arranged on liquid phase sensible heat area（1）With gas-liquid latent heat area（2）Top, gas phase sensible heat area（3）Positioned at heat exchanger
Top, gas phase sensible heat area（3）With gas-liquid latent heat area（2）Connection.
6. a kind of organic Rankine cycle power generation system composite heat exchanger as claimed in claim 1, it is characterised in that：It is described
Gas phase sensible heat area（3）Compare gas-liquid latent heat area（2）With bigger cross-sectional area, gas phase sensible heat area（3）It is undergoing phase transition
Flow media there is heat exchange by gas phase state.
7. a kind of organic Rankine cycle power generation system composite heat exchanger as claimed in claim 1, it is characterised in that：It is described
Using thermal source and the overall structure of the alternately laminated structure composition heat exchange of flow media in heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611267451.7A CN106642831A (en) | 2016-12-31 | 2016-12-31 | Composite heat exchanger for organic Rankine cycle power generating system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611267451.7A CN106642831A (en) | 2016-12-31 | 2016-12-31 | Composite heat exchanger for organic Rankine cycle power generating system |
Publications (1)
| Publication Number | Publication Date |
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| CN106642831A true CN106642831A (en) | 2017-05-10 |
Family
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| Application Number | Title | Priority Date | Filing Date |
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| CN201611267451.7A Pending CN106642831A (en) | 2016-12-31 | 2016-12-31 | Composite heat exchanger for organic Rankine cycle power generating system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3627075A3 (en) * | 2018-04-09 | 2020-07-22 | Lennox Industries Inc. | Method and apparatus for re-heat circuit operation |
| US10969145B2 (en) | 2018-04-09 | 2021-04-06 | Lennox Industries Inc. | Method and apparatus for hybrid dehumidification |
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| US5172759A (en) * | 1989-10-31 | 1992-12-22 | Nippondenso Co., Ltd. | Plate-type refrigerant evaporator |
| JP3214373B2 (en) * | 1996-10-30 | 2001-10-02 | ダイキン工業株式会社 | Flat heat transfer tube |
| US20020083734A1 (en) * | 2000-12-29 | 2002-07-04 | Cho Kyung-Il | Plate type condenser |
| JP2003322432A (en) * | 2002-05-01 | 2003-11-14 | Mitsubishi Heavy Ind Ltd | Heat exchanger and air conditioner |
| US7028762B2 (en) * | 2000-10-24 | 2006-04-18 | Mitsubishi Heavy Industries, Ltd. | Condenser for refrigerating machine |
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| WO2011061072A3 (en) * | 2009-11-23 | 2012-01-26 | BSH Bosch und Siemens Hausgeräte GmbH | Heat exchanger having a refrigerant channel |
| CN102809310A (en) * | 2012-08-15 | 2012-12-05 | 中国科学院理化技术研究所 | Regenerative heat exchanger with variable flow passage sectional area |
| CN105716331A (en) * | 2014-12-02 | 2016-06-29 | 东南大学 | Variable flow channel type heat exchanger capable of improving organic Rankine cycle efficiency |
| CN106017120A (en) * | 2015-03-31 | 2016-10-12 | 波音公司 | Condenser apparatus and method |
-
2016
- 2016-12-31 CN CN201611267451.7A patent/CN106642831A/en active Pending
Patent Citations (11)
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|---|---|---|---|---|
| US5137082A (en) * | 1989-10-31 | 1992-08-11 | Nippondenso Co., Ltd. | Plate-type refrigerant evaporator |
| US5172759A (en) * | 1989-10-31 | 1992-12-22 | Nippondenso Co., Ltd. | Plate-type refrigerant evaporator |
| JP3214373B2 (en) * | 1996-10-30 | 2001-10-02 | ダイキン工業株式会社 | Flat heat transfer tube |
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| US20020083734A1 (en) * | 2000-12-29 | 2002-07-04 | Cho Kyung-Il | Plate type condenser |
| JP2003322432A (en) * | 2002-05-01 | 2003-11-14 | Mitsubishi Heavy Ind Ltd | Heat exchanger and air conditioner |
| DE102008017113A1 (en) * | 2008-04-02 | 2009-10-08 | Behr Gmbh & Co. Kg | Evaporator for use in cooling device of heat source of motor vehicle, has plates whose length to width ratio is not greater than specific value, and refrigerant flows through flow passages in bank after reversal of direction of refrigerant |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3627075A3 (en) * | 2018-04-09 | 2020-07-22 | Lennox Industries Inc. | Method and apparatus for re-heat circuit operation |
| US10801742B2 (en) | 2018-04-09 | 2020-10-13 | Lennox Industries Inc. | Method and apparatus for re-heat circuit operation |
| US10969145B2 (en) | 2018-04-09 | 2021-04-06 | Lennox Industries Inc. | Method and apparatus for hybrid dehumidification |
| US11306928B2 (en) | 2018-04-09 | 2022-04-19 | Lennox Industries Inc. | Method and apparatus for re-heat circuit operation |
| US11788739B2 (en) | 2018-04-09 | 2023-10-17 | Lennox Industries Inc. | Method and apparatus for hybrid dehumidification |
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Application publication date: 20170510 |