EP1930667A2 - Vorrichtung zur Wärmegewinnung - Google Patents

Vorrichtung zur Wärmegewinnung Download PDF

Info

Publication number
EP1930667A2
EP1930667A2 EP20070023232 EP07023232A EP1930667A2 EP 1930667 A2 EP1930667 A2 EP 1930667A2 EP 20070023232 EP20070023232 EP 20070023232 EP 07023232 A EP07023232 A EP 07023232A EP 1930667 A2 EP1930667 A2 EP 1930667A2
Authority
EP
European Patent Office
Prior art keywords
heat
heat exchanger
temperature
boiler
transfer medium
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.)
Withdrawn
Application number
EP20070023232
Other languages
German (de)
English (en)
French (fr)
Inventor
Peter Gebhardt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IFG Solar KG
Original Assignee
IFG Solar KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by IFG Solar KG filed Critical IFG Solar KG
Publication of EP1930667A2 publication Critical patent/EP1930667A2/de
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • F24H4/04—Storage heaters
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers

Definitions

  • the invention relates to a device for heat recovery according to the preamble of patent claim 1.
  • a device for recovering heat from industrial waste heat comprising a boiler and a heat exchanger associated therewith.
  • the secondary side of the heat exchanger is connected on the one hand with a cold side and on the other hand with a hot side of the boiler, so that a closed circuit between the boiler and the heat exchanger is formed.
  • the primary side of the heat exchanger is flowed through by a heat transfer medium, which is fed by industrial waste heat.
  • this waste heat is easily enough to not only heat the water of the boiler but at the same time maintain convective flow between the boiler and the heat exchanger. Thus, no circulation pump in this cycle is required, the too strong flow would destroy the desired temperature stratification within the boiler.
  • This known device has been well proven in practice and forms the starting point of the present invention.
  • the invention has for its object to provide a device for heat recovery of the type mentioned, which is characterized by a high efficiency and wide usability of available heat sources.
  • the device according to claim 1 is used for heat recovery. It has at least one boiler containing a temperature-layered liquid.
  • the boiler is filled with water, with any other heat transfer medium is suitable.
  • the liquid in the boiler is temperature-stratified, so that there is always at least one layer of cold liquid in the boiler and above it at least one layer of warm liquid.
  • an inflow for the liquid, in particular cold water is provided on the cold side of the boiler, while on the hot side, a drain for heated liquid, in particular hot water is provided.
  • the heated liquid is used in particular for heating purposes, with alternatively or additionally also hot water for household purposes can be removed.
  • a heat exchanger To heat the liquid in the boiler, a heat exchanger is provided, the secondary side on the one hand with the Cold side and on the other hand connected to the warm side of the boiler.
  • the secondary side of the heat exchanger therefore forms a self-contained circuit with the boiler.
  • This circuit is driven solely by convection of the liquid in the boiler, so that no active circulation pump is provided.
  • This arrangement has the advantage that the flow rate of the liquid is coupled in this circuit directly to the heat input. It is therefore impossible that the liquid is circulated in this cycle, without a sufficiently high heat input occurs. Such a revolution would result in the total destruction of the temperature stratification of the liquid in the boiler, so that the withdrawal temperature of the boiler would decrease accordingly.
  • the purely convection-bound flow of this cycle requires a relatively intense heating of the liquid, since too low heating convection does not get going.
  • a heat transfer medium is used, which is evaporated by the heat source.
  • the heat transport medium is compressed by a compressor, which brings the heat transfer medium including the heat contained therein to a higher temperature.
  • the heat transfer medium is then passed through the primary side of the heat exchanger where it heats the boiler fluid.
  • the heat transport medium condenses, wherein the heat of vaporization for the heat exchanger is delivered to the boiler fluid.
  • the liquid heat transfer medium is then fed back to the heat source, where it can absorb heat again. In this way, heat is transported from the low temperature heat source to the higher temperature heat exchanger.
  • heat pump operation requires high system efficiency because of the associated energy consumption. If the heat input of the heat pump into the heat exchanger is too low, the convection in the boiler circuit does not start. On the other hand, if the heat input is too high, the compressor consumes a lot of energy without the heating of the liquid in the boiler being noticeably increased.
  • a compressor is used whose flow rate is influenced by a control device.
  • This control device is influenced by the temperature of the heat transfer medium between the output of the compressor and the output line of the heat exchanger or by the temperature of the liquid of the heat exchanger or boiler.
  • the compressor When starting up the device, therefore, the compressor is used at relatively low power to give the convection on the secondary side of the heat exchanger time to build up accordingly. With increasing Konvekomsströmung the compressor is raised in its performance, since then the heat output of the heat transfer medium increases in the heat exchanger accordingly. In this way, optimum heat utilization of the heat source results in relatively low energy consumption, so that the entire device has a surprisingly high efficiency.
  • the heat exchanger is designed as a countercurrent heat exchanger.
  • the boiler fluid is heated almost to the temperature of the heat transfer medium.
  • the heat transfer only leads to a very low temperature loss.
  • the heat exchanger is provided within a heat insulation of the boiler, the result is particularly low heat losses.
  • the heat exchanger is arranged around the boiler, so that heat radiation losses of the boiler are partly regenerated in the heat exchanger.
  • the control device is influenced by the condensation temperature of the heat transfer medium, preferably after the heat exchanger.
  • the condensation temperature is a material-dependent function of the pressure, so that only the pressure of the heat transfer medium after the heat exchanger must be measured to determine the condensation temperature in known heat transport medium. This measured pressure can then be converted to a condensation temperature using the vapor pressure curve of the heat transfer medium.
  • the knowledge of the condensation temperature is important because an incomplete condensation of the heat transfer medium would result in incomplete heat transfer into the heat exchanger and possibly an unstable control, so that the energy consumption of the compressor is too high. The influence of the condensation temperature on the control therefore improves the efficiency of the device.
  • the control device adjusts the temperature of the heat transfer medium after flowing through the heat exchanger to a temperature which is a predetermined temperature range below the condensation temperature the heat transfer medium is located.
  • the heat transfer medium is undercooled in this case, so that the heat of vaporization has been completely discharged through the heat exchanger to the boiler fluid. If the heat output in the heat exchanger increases, this results in a drop in the temperature of the heat transport medium at the outlet of the heat exchanger relative to the condensation temperature.
  • the control ensures an increase in the flow through the compressor.
  • the increased heat capacity of the heat exchanger can be used directly to increase the performance of the device.
  • the regulation remains stable over the entire operating range.
  • the temperature range a range between 1K and 10K has been proven according to claim 6. At a temperature range of less than 1K there is a risk that the condensation of the heat transfer medium is no longer complete in the event of disturbances, so that heat is pumped unused circle. In addition, this can result in difficult to control control oscillations.
  • a choice of the temperature range of over 10K is impractical, since this would result in a limitation of available heat sources. Depending on the usable heat source, however, a larger temperature range is possible.
  • the temperature range between 3K and 7K is selected to achieve the most sensitive and efficient control possible.
  • the single figure shows a schematic representation of a device 1 for heat recovery.
  • the device 1 has a boiler 2, which is filled with water 3.
  • the boiler 2 has a feed 4 for cold water and a drain 5 for hot water.
  • Inside the boiler 2 poses a layer boundary 6, in which a hot side 7 is located on a cold side 8. Between the hot side 7 and the cold side 8 only a very small mixing takes place, so that the water of the hot side 7 can be removed with a nearly constant temperature. In particular, the temperature of the water at the outlet 5 practically does not depend on the height of the layer boundary 6.
  • the boiler 2 is connected via lines 9 with a countercurrently operated heat exchanger 10.
  • the water 3 flows through a secondary side 11 of the heat exchanger 10.
  • This secondary side 11 has a larger line cross section than a primary side 12 of the heat exchanger 10 in order to be able to realize a free convection flow between the boiler 2 and the heat exchanger 10 via the lines 9 without circulating pump.
  • To achieve the lowest possible heat loss of the heat exchanger 10 is provided within a heat insulation 13 of the boiler 3.
  • the heat exchanger 10 extends around the boiler 2 around.
  • boiler 2 - could still be housed heat sources, such as heat exchangers of fossil fuel heating or high-temperature solar thermal systems.
  • heat sources such as heat exchangers of fossil fuel heating or high-temperature solar thermal systems.
  • additional heat sources in the boiler 2 have nothing to do with the subject invention itself and are therefore not shown.
  • the heat exchanger 10 could be thermally decoupled from the boiler 2 by an additional heat insulation layer.
  • the partition between the heat exchanger 10 and the boiler 2 with openings or omit entirely, so that forms an improved convection in this way.
  • the primary side 12 of the heat exchanger 10 is traversed by a heat transfer medium 14, which is circulated in a separate circuit.
  • the primary side 12 of the heat exchanger 10 is connected via a line 15 with a container 15 a, which is designed as an intermediate heat exchanger.
  • the heat transfer medium 14 releases heat to vaporized heat transfer medium 14, which flows through the container 15a in a line 22.
  • This measure name improves the heat absorption capacity of the heat transport medium 14.
  • the heat transfer medium 14 After leaving the container 15 a, the heat transfer medium 14 enters an expansion valve 16, which ensures a reduction in the pressure of the heat transfer medium 14.
  • the expansion valve 16 is connected via a control device 17 with a pressure gauge 18 in operative connection, which keeps the pressure of the heat transfer medium in the conduit 15 constant.
  • the control device 17 is preceded by a differential amplifier 17b, which compares the measured pressure with a desired value of a setpoint generator 17a. The comparison result is the controlled variable of the control device 17. This ensures that within the heat exchanger 10 in approximately constant pressure conditions of the heat transfer medium 14 prevail, so that the heat transfer medium 14 has approximately a constant condensation temperature.
  • the expansion valve 16 is connected via a line 19 with another heat exchanger 20 in operative connection, which is in contact with a heat source 21.
  • a heat source 21 is, for example, ambient air, but also geothermal or a solar thermal system in question.
  • the temperature of the heat source 21 is not sufficient to directly heat the water 3 in the heat exchanger 10. For this purpose, this heat must first be brought to a higher temperature.
  • the heat transfer medium 14 is chosen so that it is liquid within the conduit 19 and evaporated by the heat source 21. This steam is passed through a further line 22 through the container 15 a, where it is in heat exchange with the coming out of the heat exchanger 10 heat transport medium 14. The heat transfer medium 14 is heated approximately to the Zulaüftemperatur of the boiler 2.
  • the heat transfer medium 14 After leaving the container 15a, the heat transfer medium 14 is fed to a compressor 23, whose flow is adjustable over the speed.
  • the compressor 23 compresses the heat transfer medium 14, which also increases its temperature level.
  • the heat transfer medium 14 passes back into the heat exchanger 10, where it gives off its heat to the secondary side water 3.
  • the heat transfer medium condenses 14, so that its entire heat of vaporization is released to the water.
  • the heat exchanger 10 Due to the design of the heat exchanger 10 as a countercurrent heat exchanger is also achieved that the water 3 after leaving the heat exchanger 10 has almost the temperature of the incoming heat transfer medium 14. The loss of temperature is very low, since the incoming heat transfer medium 14 initially heated only the uppermost layer of the water 3, which has already reached almost the temperature of the heat transfer medium 14.
  • the heat transfer medium 14 flows downwards in the heat exchanger and heats ever colder water layers, whereby it cools rapidly.
  • the condensation temperature of the heat transfer medium 14 is reached at a certain point within the heat exchanger 10, so that instead of a further cooling of the heat transfer medium 14, a condensation of the same uses at a constant temperature.
  • the condensation of the heat transfer medium 14 is complete, so that the entire heat of evaporation is released.
  • the now liquid heat transport medium 14 is cooled further and then fed to the expansion valve 16 and the heat source 21. In this way, a very efficient use of energy of the device 1 results.
  • a temperature sensor 25 in the region of the line 15 is provided on the output side of the heat exchanger 10.
  • This temperature sensor 25 measures the temperature of the heat transfer medium 14 after the heat release in the heat exchanger 10.
  • the condensation temperature of the heat transfer medium 14 is calculated therefrom via an arithmetic circuit 26, in which the vapor pressure curve of the heat transport medium 14 is stored, and emitted as an electrical signal.
  • the calculated condensation temperature is supplied together with the signal of the temperature sensor 25 and a desired value of a setpoint generator 27a to a differential amplifier 27, which determines therefrom the supercooling of the heat transfer medium 14 in the line 15 below the condensation temperature and compares it with the desired value ,
  • An output signal 28 of the differential amplifier 27 is fed to a control device 29, which drives the compressor 23 via a frequency converter 30.
  • a control device 29 which drives the compressor 23 via a frequency converter 30.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Central Heating Systems (AREA)
EP20070023232 2006-11-30 2007-11-30 Vorrichtung zur Wärmegewinnung Withdrawn EP1930667A2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200620018320 DE202006018320U1 (de) 2006-11-30 2006-11-30 Vorrichtung zur Wärmegewinnung

Publications (1)

Publication Number Publication Date
EP1930667A2 true EP1930667A2 (de) 2008-06-11

Family

ID=37896854

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070023232 Withdrawn EP1930667A2 (de) 2006-11-30 2007-11-30 Vorrichtung zur Wärmegewinnung

Country Status (5)

Country Link
EP (1) EP1930667A2 (ru)
CN (1) CN101191664A (ru)
CA (1) CA2612787A1 (ru)
DE (1) DE202006018320U1 (ru)
EA (1) EA013454B1 (ru)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009026420B4 (de) 2009-05-22 2023-10-05 Joachim Zeeh Mehrzonen-Schichtladespeicher
DE102009043583A1 (de) 2009-09-30 2011-03-31 Höcker, Hans-Peter, Dipl.-Ing.(FH) Wärmetauscher für Kältemittel

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6091155A (ja) * 1983-10-25 1985-05-22 Matsushita Electric Ind Co Ltd 給湯装置
US6460358B1 (en) * 2000-11-13 2002-10-08 Thomas H. Hebert Flash gas and superheat eliminator for evaporators and method therefor
JP2004347148A (ja) * 2003-05-20 2004-12-09 Matsushita Electric Ind Co Ltd ヒートポンプ給湯装置
JP2005098546A (ja) * 2003-09-22 2005-04-14 Matsushita Electric Ind Co Ltd ヒートポンプ給湯装置

Also Published As

Publication number Publication date
DE202006018320U1 (de) 2007-03-15
CA2612787A1 (en) 2008-05-30
EA013454B1 (ru) 2010-04-30
EA200702393A1 (ru) 2008-06-30
CN101191664A (zh) 2008-06-04

Similar Documents

Publication Publication Date Title
DE2754626C2 (de) Mit einer Energiequelle relativ niedriger Temperatur, insbesondere Solarenergie, arbeitende Kälteanlage
AT502029B1 (de) Einrichtung zur belüftung und beheizung von gebäuden
DE2748415C2 (de) Heizverfahren und bimodales Heizsystem zum Heizen von Gebäuden
EP2053242A2 (de) Verfahren zum Betreiben eines solarthermischen Kraftwerks und solarthermisches Kraftwerk
DE2122064A1 (de) Kühlanlage, Wärmerückgewinnungsanlage, Verdichtungsanlage für gekühltes Gas und Anlage zur Durchführung eines Brayton-Kreisprozesses
DE102011108970A1 (de) Niedertemperaturkraftwerk, sowie Verfahrenzum Betrieb desselben
EP0288695B1 (de) Brennwert-Heizkessel und Verfahren zu seinem Betreiben
DE2854055A1 (de) Verfahren zum erhitzen eines waermetraegers mit einer absorptionswaermepumpe
DE102006056979B4 (de) Vorrichtung zur Wärmegewinnung
EP2287547B1 (de) Wärmepumpe und Verfahren zur Regelung der Quelleneintrittstemperatur an der Wärmepumpe
EP1930667A2 (de) Vorrichtung zur Wärmegewinnung
DE2846797A1 (de) Vorrichtung zur waermerueckgewinnung
DE2649872A1 (de) Waermepumpe zur erzeugung von nutzwaerme und nutzkaelte mit energiespeicherung unter ausnutzung der erstarrungs- bzw. schmelzwaerme von wasser
EP1736720A2 (de) Luftwärmepumpen-Verdampfungsvorrichtung für eine Luftwärmepumpenheizung sowie Verfahren zum Betreiben einer Luftwärmepumpenheizung
DE2613418A1 (de) Drehverdampfer
DE2538730A1 (de) Kuehlwaerme-rueckgewinnungsanlage
DE4408087C2 (de) Verfahren zum Betrieb einer Wärmeaustauscheranlage, für rekuperativen Wärmeaustausch
WO2012000002A2 (de) Anordnung zum umwandeln thermischer energie und vorrichtung zum erwärmen und kühlen eines mediums
CH626426A5 (en) Internal combustion engine system with a pressure-charged, water-cooled engine
EP2083169A1 (de) Kraftwerk sowie Verfahren zur Gewinnung von mechanischer oder elektrischer Energie
DE102020117462B4 (de) Verfahren zum Betreiben einer Absorptionswärmepumpe
DE19861020C1 (de) Lüftungsanordnung für Gebäude
DE4138774A1 (de) Waermepumpe
DE102013001652A1 (de) Verfahren und Verarbeitungsvorrichtung für Verbrennungsstoffe aus einer Wärmequelle
DE202010010599U1 (de) Vorrichtung zur Wärmegewinnung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20110601