EP2321589A1 - Hochtemperaturwärmepumpe und verfahren zu deren regelung - Google Patents
Hochtemperaturwärmepumpe und verfahren zu deren regelungInfo
- Publication number
- EP2321589A1 EP2321589A1 EP09736109A EP09736109A EP2321589A1 EP 2321589 A1 EP2321589 A1 EP 2321589A1 EP 09736109 A EP09736109 A EP 09736109A EP 09736109 A EP09736109 A EP 09736109A EP 2321589 A1 EP2321589 A1 EP 2321589A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant
- temperature
- hot water
- gas cooler
- heat exchanger
- 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.)
- Granted
Links
- 238000000034 method Methods 0.000 title claims description 18
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims abstract description 110
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 86
- 229910002092 carbon dioxide Inorganic materials 0.000 claims abstract description 55
- 239000001569 carbon dioxide Substances 0.000 claims abstract description 55
- 238000002347 injection Methods 0.000 claims abstract description 18
- 239000007924 injection Substances 0.000 claims abstract description 18
- 239000012530 fluid Substances 0.000 claims abstract description 6
- 239000002826 coolant Substances 0.000 claims abstract 10
- 239000003507 refrigerant Substances 0.000 claims description 88
- 238000010438 heat treatment Methods 0.000 claims description 13
- 230000004941 influx Effects 0.000 claims description 4
- 230000008569 process Effects 0.000 claims description 4
- 238000004146 energy storage Methods 0.000 claims description 3
- 238000001704 evaporation Methods 0.000 claims description 3
- 230000008020 evaporation Effects 0.000 claims description 3
- 238000010992 reflux Methods 0.000 claims 1
- 238000013021 overheating Methods 0.000 abstract description 5
- 238000010792 warming Methods 0.000 abstract description 2
- 238000010586 diagram Methods 0.000 description 7
- 230000033228 biological regulation Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- GOOHAUXETOMSMM-UHFFFAOYSA-N Propylene oxide Chemical compound CC1CO1 GOOHAUXETOMSMM-UHFFFAOYSA-N 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 239000001273 butane Substances 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000002360 explosive Substances 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- IJDNQMDRQITEOD-UHFFFAOYSA-N n-butane Chemical compound CCCC IJDNQMDRQITEOD-UHFFFAOYSA-N 0.000 description 1
- OFBQJSOFQDEBGM-UHFFFAOYSA-N n-pentane Natural products CCCCC OFBQJSOFQDEBGM-UHFFFAOYSA-N 0.000 description 1
- 239000001294 propane Substances 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 231100000331 toxic Toxicity 0.000 description 1
- 230000002588 toxic effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- 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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- 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 high-temperature heat pump for heating a fluid, preferably water, to a temperature level up to 150 0 C, which is operated with carbon dioxide as the refrigerant in the trans-critical range.
- the heat pump is particularly suitable for industrial heat generation and heat recovery as well as for energy storage methods where hot water is used as the storage medium.
- Carbon dioxide is a natural refrigerant and is characterized by a much lower global warming potential than conventional refrigerants, such. Hydrofluorocarbons, off.
- carbon dioxide is not toxic, e.g. Ammonia and propylene ether, nor can it form explosive mixtures with air, e.g. Propane and butane.
- the critical point of carbon dioxide is 31, 1 0 C and 73.6 bar. Since heat pumps are almost always used to generate higher temperatures, they are inevitably operated in the transcritical range.
- a heat pump is described, the refrigerant circuit is operated with a desuperheater, an evaporator, a compressor and a throttle body in the supercritical range.
- the heat pump has a control unit for controlling the throttle body.
- the throttle body is operated in response to a first pressure on the high-pressure side of the refrigerant circuit when a permissible overheating of the refrigerant in the refrigerant circuit is present. If the refrigerant in the refrigerant circuit is outside the allowable superheat, the throttle body is operated in accordance with a first temperature before the compressor.
- WO 2004/057245 A1 describes a heat pump in which, by overheating the refrigerant upstream of the suction side of the compressor, an increase in the temperature of the refrigerant at the outlet of the compressor is effected without the pressure of the refrigerant on the output side of the compressor being additionally increased.
- the overheating should be achieved for example with a countercurrent heat exchanger.
- the desired heating of water to 60-90 0 C is achieved.
- EP 1 396 689 A1 discloses a refrigerant circuit consisting of a compressor, a heat exchanger, a refrigerant collector, an expansion valve and an evaporator. To further cool the refrigerant after exiting the heat exchanger and before entering the refrigerant receiver, this flows through an internal heat exchanger. The energy extracted from the refrigerant is returned to the refrigerant after it has left the evaporator and before it re-enters the compressor. In the case of carbon dioxide heat pumps with smaller outputs in the range from 5 to 50 kW, which are used to supply single and multi-family houses with hot water and for heating, a high-pressure regulation is usually installed.
- the evaporator is followed by a refrigerant collector, which receives from the evaporator leaking liquid carbon dioxide.
- a refrigerant collector which receives from the evaporator leaking liquid carbon dioxide.
- the invention has for its object to provide a run with carbon dioxide as a refrigerant heat pump, which allows simultaneous control of the refrigerant superheating in the evaporator, the high pressure in the gas cooler system and the heating of the refrigerant upstream of the compressor by internal heat exchanger, whereby high hot water outlet temperatures can be achieved , With the method high performance numbers should be achievable.
- the heat pump consists of an evaporator, at least two internal heat exchangers, a compressor, one or more series-connected gas coolers, a refrigerant collector and at least one refrigerant injection valve.
- the inlet of the refrigerant collector is connected via a control valve (and via the first inner heat exchanger) to the (refrigerant side) outlet of the series connection of the gas cooler and the outlet of the refrigerant collector to the refrigerant injection valve.
- the coefficient of performance of the heat pump reaches its maximum value at a certain level of pressure in the gas cooler. If the pressure increases further, the hot water outlet temperature increases, but the coefficient of performance decreases. - A -
- control loop is also used to increase the hot water outlet temperature by raising the pressure.
- the pressure is increased only so far that the required hot water outlet temperature is reached exactly.
- a second application-related inner heat exchanger the carbon dioxide is heated by the hot water generated by the heat pump used.
- the second internal heat exchanger is connected on the refrigerant side between the outlet of the first internal heat exchanger and the inlet of the compressor. On the water side, its inlet is connected via at least one 3-way valve to one of the water-side outlets of the gas cooler.
- the second internal heat exchanger is preferably connected to the gas cooler water outlet side, the refrigerant side output is connected via the first inner heat exchanger to the refrigerant collector; This gas cooler produces the water with the lowest temperature level.
- the refrigerant superheating on the influx of the refrigerant in the evaporator and the high pressure in the gas cooler controlled by the volume flow of carbon dioxide from the gas cooler in the refrigerant collector.
- the pressure and the temperature of the carbon dioxide at the outlet of the evaporator is measured, from which the refrigerant superheat is determined and compared in a control unit with a setpoint. If the target value is undershot, the influx of carbon dioxide into the evaporator is throttled by means of a refrigerant injection valve; if it is exceeded, the inflow is correspondingly increased by opening the refrigerant injection valve.
- the refrigerant injection valve of the evaporator either a pressure-controlled thermostatic valve or an electronic valve is used, which is controlled by means of temperature sensors for the evaporation temperature and the refrigerant outlet temperature from the evaporator.
- the high pressure is measured in one of the refrigerant pipes between the compressor outlet and the refrigerant collector with a pressure sensor arranged there.
- the actual value is compared with the setpoint. If no increase in temperature of the hot water is required by an increase in pressure in the gas cooler, the setpoint corresponds to the pressure value at which the heat pump works with maximum coefficient of performance; otherwise it is, according to the necessary increase in temperature, above.
- the setpoint is undershot, the flow of carbon dioxide from the gas cooler into the refrigerant collector is throttled by means of the control valve arranged between the gas cooler outlet and the refrigerant collector; if it is exceeded, the flow of carbon dioxide is correspondingly increased.
- a stepwise regulation of the heat pump to the temperature value of the hot water is provided.
- the temperature of the hot water is measured and compared in a controller with a setpoint. If the setpoint is exceeded, more is done by means of a 3-way valve with actuator and one by-pass and Passed less carbon dioxide past the first and the second internal heat exchanger.
- the volume flow of hot water through the second inner heat exchanger is additionally increased by means of another 3-way valve with actuator.
- the pressure in the gas cooler is increased.
- the target temperature of the hot water is not reached, although the entire refrigerant flow is already passed through the first and the second heat exchanger and the volume flow of hot water through the second inner heat exchanger and the pressure in the gas cooler have reached their maximum control limits, then the last hot water volume flow reduced by the gas cooler.
- the hot water volume flow through the gas cooler is adjusted via the speed of the water pump of the water cycle, by means of a throttle valve or via a controllable by a 3-way valve bypass to the water pump, which causes a partial return of the hot water.
- Ts diagram temperature-entropy diagram
- the cooling of the carbon dioxide in the gas cooler takes place along a curved line.
- the resulting heating of the water takes place in the Ts-diagram along straight line sections that run below the curved line of the carbon dioxide.
- the area lying between the curved line and the straight line sections represents the power loss occurring during the heat transfer process. Consequently, the more accurately the curved line of carbon dioxide is followed with a number n of straight sections, the more effectively the heat transfer becomes.
- n gas coolers are required for this purpose, which each heat water to n different temperature levels. It is therefore in each case to weigh the expenditure on equipment against the achieved thereby increasing the efficiency.
- n gas coolers energy can be stored with relatively high efficiency and removed again by the heated by the gas cooler water with n different temperature levels stored in n separate hot water tanks and to remove the energy of a water-powered with carbon dioxide heat engine with n evaporators is supplied.
- the n temperature values of the gas cooler and the evaporator must correlate with respect to the refrigerant circuit.
- the hot water with n temperature levels is used to supply industrial plants specifically with water to the temperature levels required for the individual steps of the production process.
- the heat pump should be used primarily for the production of hot water with a temperature of 65 ° C. If the demand is met, the heat pump can also support the heating of the building. This is z. B. at a floor heating a flow temperature of 40 0 C sufficient. In this case, the flow temperature is regulated down in reverse order by means of the control circuits.
- Fig. 1 system diagram of a heat pump with two gas coolers
- Fig. 2 T-s diagram of the heat pump process of a heat pump with two gas coolers.
- the carbon dioxide flows to the 3-way valve 18, which is controlled by means of the regulator 16, in which the temperature value of the hot water tnwA2 (or tnwAi) is compared with a predetermined desired value, and the actuator 17. If the real temperature value of the water is higher than the setpoint value, the 3-way valve 18 is adjusted so that more carbon dioxide is led past the series connection of the first inner heat exchanger 4 and second inner heat exchanger 5 via the bypass 9. If the real temperature value is lower, more carbon dioxide is conducted through the internal heat exchangers 4, 5 to the compressor 1.
- the pressure of the carbon dioxide is increased from about 45 to about 130 bar.
- the temperature of the carbon dioxide rises from less than 50 to up to 150 c C.
- the up to 150 0 C hot carbon dioxide is first passed through the first gas cooler 2 and then through the second gas cooler 3.
- the gas cooler 2, 3 act as a heat exchanger, so that cooled in the first gas cooler 2, the carbon dioxide and hot water at a temperature t ⁇ w A2 up to 145 ° C and hot gas in the gas cooler 3 with a temperature t ⁇ w A i of about 70 0 C generated becomes.
- the carbon dioxide passes through the first inner heat exchanger 4 via the control valve 15 in the refrigerant collector 7.
- the control valve 15 is the regulator 13, the high pressure in one of the refrigerant lines between the outlet of the compressor 1 and the entry into the Control valve 15 measures and compares this with the setpoint of the high pressure, controlled.
- the pressure in the gas coolers 2, 3 is at a fall below the setpoint increased by that by means of the control valve 15 and the actuator 14, the flow of the effluent from the gas cooler carbon dioxide is throttled. If the setpoint is exceeded, the flow of the effluent carbon dioxide is increased accordingly.
- the carbon dioxide is directed to the refrigerant injection valve 8 of the evaporator 6, which is controlled by the electronic control unit 12.
- the control unit 12 measures via temperature sensors, the evaporation temperature and the refrigerant outlet temperature from the evaporator 6 and determines from the refrigerant superheat (overheating of carbon dioxide). This is compared with a setpoint. If the setpoint is undershot, the influx of carbon dioxide to the evaporator 6 is throttled by means of the refrigerant injection valve 8 and increased when it is exceeded by opening the refrigerant injection valve 8.
- the incoming amount of water is regulated.
- the controller 19 the current temperature value THW A2 is (or W A O measured and compared with the predetermined desired value. If the 3-way valves 18 and 24 are controlled already by means of the regulator 16 and the control valve 15 by the controller 13 to the control limit are, but the target value is not yet reached, the amount of water through the bypass 22 is increased by means of the 3-way valve 21.
- control unit evaporator injection
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200810046620 DE102008046620B4 (de) | 2008-09-10 | 2008-09-10 | Hochtemperaturwärmepumpe und Verfahren zu deren Regelung |
PCT/DE2009/001210 WO2010028622A1 (de) | 2008-09-10 | 2009-08-28 | Hochtemperaturwärmepumpe und verfahren zu deren regelung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2321589A1 true EP2321589A1 (de) | 2011-05-18 |
EP2321589B1 EP2321589B1 (de) | 2015-08-26 |
Family
ID=41527065
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09736109.1A Active EP2321589B1 (de) | 2008-09-10 | 2009-08-28 | Hochtemperaturwärmepumpe und verfahren zu deren regelung |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2321589B1 (de) |
DE (1) | DE102008046620B4 (de) |
WO (1) | WO2010028622A1 (de) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102345941B (zh) * | 2010-08-03 | 2014-08-13 | 昆山台佳机电有限公司 | 一种中央空调制冷剂侧切换的满液式水源热泵机组 |
DE102011086476A1 (de) * | 2011-09-30 | 2013-04-04 | Siemens Aktiengesellschaft | Hochtemperaturwärmepumpe und Verfahren zur Verwendung eines Arbeitsmediums in einer Hochtemperaturwärmepumpe |
DE102012015647A1 (de) | 2012-08-07 | 2014-02-13 | Frank Mayer | Hochtemperaturwärmepumpe |
DE102013203243A1 (de) * | 2013-02-27 | 2014-08-28 | Siemens Aktiengesellschaft | Wärmepumpe und Verfahren zum Betreiben einer Wärmepumpe |
DE102013214891A1 (de) * | 2013-07-30 | 2015-02-05 | Siemens Aktiengesellschaft | Wärmetechnische Verschaltung einer Geothermiequelle mit einem Fernwärmenetz |
CN108105833A (zh) * | 2018-01-31 | 2018-06-01 | 天津商业大学 | 一种机械辅助过冷co2跨临界热泵供暖系统 |
DE102019126983A1 (de) * | 2019-10-08 | 2021-04-08 | Wolf Gmbh | Wärmepumpe mit Temperaturregelung und Verfahren zur Nutzung von Umgebungswärme durch eine Wärmepumpe |
CN110966783A (zh) * | 2019-12-23 | 2020-04-07 | 江苏苏净集团有限公司 | 一种双级节流多温二氧化碳热泵机组 |
CN112503765A (zh) * | 2020-12-17 | 2021-03-16 | 广东高美空调设备有限公司 | 一种二氧化碳热泵供水机组 |
NL1044144B1 (nl) | 2021-09-07 | 2023-03-21 | Werkenhorst B V | Warmtepompinstallatie en werkwijze voor het verwarmen van een medium |
DE102021123631A1 (de) | 2021-09-13 | 2023-03-16 | Lübbers Anlagen- und Umwelttechnik GmbH | Trocknungsvorrichtung zum Bereitstellen eines Prozessgases für eine Trockneranlage |
DE102022121699A1 (de) | 2022-08-26 | 2024-02-29 | Konvekta Aktiengesellschaft | Wärmepumpenanlage mit mehrstufiger Wärmeübertragung und Verfahren dazu |
DE102022127011A1 (de) | 2022-10-14 | 2024-04-25 | Lübbers FTS GmbH | Wärmepumpenvorrichtung zum energieeffizienten Erzeugen einer Prozesswärme, Trocknervorrichtung zum Trocknen eines zu trocknenden Gutes und Verfahren zum Betreiben einer Wärmepumpenvorrichtung |
DE102022132130A1 (de) | 2022-12-05 | 2024-06-06 | Audi Aktiengesellschaft | Kälteanlage mit Wärmepumpenfunktion und im Wärmepumpenbetrieb durchströmtem Bypassabschnitt, Kraftfahrzeug mit einer solchen Kälteanlage |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3615475B2 (ja) * | 2000-09-28 | 2005-02-02 | 三洋電機株式会社 | ヒートポンプ給湯機 |
JP2002162123A (ja) | 2000-11-21 | 2002-06-07 | Sekisui Chem Co Ltd | ヒートポンプ |
JP3801006B2 (ja) * | 2001-06-11 | 2006-07-26 | ダイキン工業株式会社 | 冷媒回路 |
NO318864B1 (no) * | 2002-12-23 | 2005-05-18 | Sinvent As | Forbedret varmepumpesystem |
JP4058696B2 (ja) * | 2004-05-28 | 2008-03-12 | 日立アプライアンス株式会社 | ヒートポンプ給湯システム |
DE102005044029B3 (de) * | 2005-09-14 | 2007-03-22 | Stiebel Eltron Gmbh & Co. Kg | Wärmepumpe |
-
2008
- 2008-09-10 DE DE200810046620 patent/DE102008046620B4/de active Active
-
2009
- 2009-08-28 WO PCT/DE2009/001210 patent/WO2010028622A1/de active Application Filing
- 2009-08-28 EP EP09736109.1A patent/EP2321589B1/de active Active
Non-Patent Citations (1)
Title |
---|
See references of WO2010028622A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2010028622A4 (de) | 2010-05-14 |
WO2010028622A1 (de) | 2010-03-18 |
DE102008046620B4 (de) | 2011-06-16 |
EP2321589B1 (de) | 2015-08-26 |
DE102008046620A1 (de) | 2010-03-18 |
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