EP2321589B1 - Pompe à chaleur haute température et son procédé de réglage - Google Patents

Pompe à chaleur haute température et son procédé de réglage Download PDF

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Publication number
EP2321589B1
EP2321589B1 EP09736109.1A EP09736109A EP2321589B1 EP 2321589 B1 EP2321589 B1 EP 2321589B1 EP 09736109 A EP09736109 A EP 09736109A EP 2321589 B1 EP2321589 B1 EP 2321589B1
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Prior art keywords
temperature
hot water
coolant
heat exchanger
carbon dioxide
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EP09736109.1A
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German (de)
English (en)
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EP2321589A1 (fr
Inventor
Eberhard Wobst
Steffen Oberländer
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Thermea Energiesysteme GmbH
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Thermea Energiesysteme GmbH
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    • 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 ° C, which is operated with carbon dioxide as a 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 ° C and 73.6 bar. Since heat pumps are almost always used to generate higher temperatures, they are inevitably operated in the transcritical range.
  • DE 10 2005 044 029 B3 is a heat pump 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 is a heat pump is described in which caused by overheating of the refrigerant upstream of the suction side of the compressor, an increase in the temperature of the refrigerant at the outlet of the compressor, without the pressure of the refrigerant is additionally increased on the output side of the compressor.
  • the overheating should be achieved for example with a countercurrent heat exchanger.
  • the desired heating of water to 60-90 ° 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.
  • JP 2002 162123 A a run with carbon dioxide as a high-temperature heat pump with an evaporator, at least one internal heat exchanger, a compressor, three series condensers (gas cooler), a refrigerant collector and a refrigerant injection valve shown, in which the input of the refrigerant collector via a controllable expansion valve and the first inner Heat exchanger with the outlet of the series circuit of the gas cooler and the outlet of the refrigerant collector is connected to the expansion valve.
  • Another internal heat exchanger which serves to heat the carbon dioxide before entering the compressor by means of hot water, is connected on the refrigerant side between the outlet of the first internal heat exchanger and the inlet of the compressor. With the heat pump, temperatures up to 150 ° C should be achievable.
  • the invention has for its object to provide a powered with carbon dioxide refrigerant heat pump, which allows simultaneous control of refrigerant superheat 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 starting point is a high-temperature heat pump for heating a fluid to temperatures of up to 150 ° C, which is operated with carbon dioxide as the refrigerant in the transcritical range. It is intended to use preferably water as the fluid, which is heated to temperatures of 100 to 130 ° C.
  • 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.
  • the control loop is also used to increase the hot water outlet temperature by raising the pressure. In order to keep the resulting reduction in the coefficient of performance as low as possible, the pressure is increased only so far that the required hot water outlet temperature is reached exactly.
  • a second application-related internal heat exchanger in addition to the first inner heat exchanger, which causes a preheating of the carbon dioxide flowing to the compressor by the flowing back from the gas cooler carbon dioxide to the carbon dioxide before To further heat the inlet to the compressor, a second application-related internal heat exchanger, in which 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.
  • the gas cooler each heat the water to different temperature levels and for preheating the carbon dioxide, a high temperature level is required, the water-side inlet of the second internal heat exchanger via at least one control valve (3-way valve) connected to the gas cooler water outlet side, the refrigerant side output over the first inner heat exchanger is connected to the refrigerant collector; This gas cooler produces the water with the lowest temperature level.
  • the refrigerant superheating is controlled via the inflow of the refrigerant into the evaporator and the high pressure in the gas cooler via the volume flow of carbon dioxide from the gas cooler into 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.
  • a pressure sensor arranged there.
  • the actual value 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 passed by means of a 3-way valve with actuator and one by-pass, and less if less carbon dioxide is passed by the first and second internal heat exchangers.
  • 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 hot water volume flow is reduced by the gas cooler last.
  • 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.
  • T-s diagram temperature-entropy diagram
  • the cooling of carbon dioxide in the gas cooler takes place along a curved line.
  • the resulting heating of the water takes place in the T-s 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 in the heat transfer process. Consequently, the more accurately the curved line of the carbon dioxide is followed with a number n of straight line 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 comparatively 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 ° C is sufficient. In this case, the flow temperature is regulated down in reverse order by means of the control circuits.
  • 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 t HWA2 (or t HWA1 ) is compared with a predetermined desired value, and the actuator 17. If the real temperature value of the water is higher than the set value, the 3-way valve 18 is set so that more carbon dioxide through the bypass 9 on the series connection of the first inner heat exchanger 4 and second inner heat exchanger 5 is passed. 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 up to 150 ° C.
  • the up to 150 ° 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 HWA2 up to 145 ° C and hot gas in the gas cooler 3 with a temperature t HWA1 of about 70 ° C is generated ,
  • 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 increased by falling below the setpoint, 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 second gas cooler 3 After leaving the second gas cooler 3, part of the water, which now has the temperature t HWA1 (also called the mean temperature), is diverted by means of the 3-way valve 10. The remaining water is passed to the 3-way valve 24, which divides the water flow into a flow through the first gas cooler 2 and a flow through the second inner heat exchanger 5.
  • the 3-way valve 24 and the actuator 23 By means of the 3-way valve 24 and the actuator 23, the water flow through the second inner heat exchanger 5 is increased if the current temperature value t HWA2 (or t HWA1 ) is below the setpoint and already by means of the 3-way valve 18 the entire carbon dioxide is passed through the series connection of the two inner heat exchanger 4, 5.

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  • 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)

Claims (13)

  1. Pompe à chaleur haute température pour le chauffage d'un fluide à un niveau de température jusqu'à 150 °C, qui fonctionne avec du dioxyde de carbone dans la zone transcritique en tant que réfrigérant, avec un évaporateur (6), au moins un échangeur de chaleur interne (4), un compresseur (1), un ou plusieurs refroidisseurs de gaz (2, 3) montés en série, un accumulateur de produit réfrigérant (7) et une soupape d'injection de produit réfrigérant (8), dans laquelle l'entrée de l'accumulateur de produit réfrigérant (7) est reliée avec la sortie du montage en série des refroidisseurs de gaz (2, 3) par l'intermédiaire d'une soupape de réglage (15) ainsi que par l'intermédiaire du premier échangeur de chaleur interne (4), et la sortie de l'accumulateur de produit réfrigérant (7) est reliée avec la soupape de détente (8), et un autre échangeur de chaleur interne (5) répondant aux besoins qui sert au chauffage du dioxyde de carbone avant l'entrée dans le compresseur (1) au moyen d'eau chaude, qui est branché du côté du produit réfrigérant entre la sortie du premier échangeur de chaleur interne (4) et l'entrée du compresseur (1), caractérisée en ce que l'entrée du côté de l'eau du deuxième échangeur de chaleur interne (5) est reliée avec le refroidisseur de gaz (3) étant situé à la sortie du côté de l'eau par l'intermédiaire d'au moins une soupape de réglage (24), dont la sortie du coté du produit réfrigérant est raccordée au premier échangeur de chaleur interne (4).
  2. Procédé de régulation d'une pompe à chaleur haute température selon la revendication 1, caractérisé en ce que
    - la pression du produit réfrigérant (po) et la température du produit réfrigérant (to) sont mesurées à la sortie de l'évaporateur (6), on en déduit la surchauffe du produit réfrigérant et celle-ci est comparée à une valeur souhaitée dans une unité de régulation (12), où lors d'une valeur inférieure à la valeur souhaitée, le flux d'arrivée du dioxyde de carbone vers l'évaporateur (6) est limité par un étranglement et est augmenté pour un dépassement par l'ouverture de la soupape d'injection de produit réfrigérant (8),
    - la haute pression (pKKA) est mesurée dans l'une des conduites de produit réfrigérant entre la sortie de compresseur et l'entrée dans la soupape de réglage (15), la valeur réelle est comparée avec une valeur souhaitée au moyen du régulateur (13), valeur souhaitée qui, si aucune élévation de la température de l'eau chaude par une augmentation de la pression dans les refroidisseurs de gaz (2, 3) n'est nécessaire, correspond à la valeur de la pression à laquelle la pompe à chaleur haute température travaille avec un rendement maximal, et autrement est supérieure à cette valeur de pression correspondant à l'élévation de température nécessaire, dans lequel, pour une valeur inférieure à la valeur souhaitée le flux de dioxyde de carbone provenant des refroidisseurs de gaz (2, 3) est limité par étranglement dans l'accumulateur de produit réfrigérant (7) au moyen de la soupape de réglage (15) disposée entre l'échangeur de chaleur interne (4) et l'accumulateur de produit réfrigérant (7), et est augmenté pour une valeur supérieure.
  3. Procédé selon la revendication 2, caractérisé en ce qu'une soupape thermostatique réglée par la pression est insérée en tant soupape d'injection de produit réfrigérant (8).
  4. Procédé selon la revendication 2, caractérisé en ce qu'une soupape électronique est employée en tant que soupape d'injection de produit réfrigérant (8), qui est régulée au moyen de capteurs de température pour la température d'évaporation et la température de sortie du produit réfrigérant provenant de l'évaporateur (6).
  5. Procédé selon les revendications 2 à 4, caractérisé en ce que la température de l'eau chaude est mesurée et comparée à une valeur souhaitée dans le régulateur (16), dans lequel, pour un dépassement de la valeur souhaitée, davantage de dioxyde de carbone est apporté dans le premier (4) et le deuxième échangeur de chaleur (5) et pour une valeur inférieure, moins de dioxyde de carbone y est amené.
  6. Procédé selon la revendication 5, caractérisé en ce que, dans le cas où déjà le flux de produit réfrigérant total a traversé le premier (4) et le deuxième échangeur de chaleur interne (5) au moyen d'une soupape à trois voies (18) pour des volumes d'écoulement élevés d'eau chaude, et où la température souhaitée de l'eau chaude n'est pas atteinte, le volume d'écoulement de l'eau chaude à travers le deuxième échangeur de chaleur interne (5) est augmenté au moyen d'une soupape à 3 voies (24) avec un actuateur (23).
  7. Procédé selon la revendication 6, caractérisé en ce que, si le volume d'écoulement de l'eau chaude à travers le deuxième échangeur de chaleur interne (5) est arrivé à sa valeur maximale et si la température souhaitée de l'eau chaude n'est pas atteinte, la pression est augmentée dans les refroidisseurs de gaz (2, 3).
  8. Procédé selon la revendication 7, caractérisé en ce que, si les pressions dans les refroidisseurs de gaz (2, 3) sont arrivées à leurs valeurs maximales et si la température souhaitée de l'eau chaude n'est pas atteinte, le volume d'écoulement d'eau chaude à travers les refroidisseurs de gaz (2, 3) est diminué.
  9. Procédé selon la revendication 8, caractérisé en ce que le volume d'écoulement d'eau chaude à travers les refroidisseurs de gaz (2, 3) est réglé par l'intermédiaire d'un by-pass (22) pour l'eau chaude réglable au moyen du régulateur (19), de l'actuateur (20) et de la soupape à 3 voies (21), qui provoque un reflux partiel de l'eau chaude.
  10. Procédé selon la revendication 8, caractérisé en ce que le volume d'écoulement de l'eau chaude à travers les refroidisseurs de gaz (2, 3) est réglé par l'intermédiaire du nombre de tours d'une pompe à eau (11 ) du circuit d'eau ou au moyen d'une soupape d'étranglement.
  11. Utilisation de la pompe à chaleur selon la revendication 1 pour le stockage d'énergie, où la pompe à chaleur présente n refroidisseurs de gaz qui alimentent respectivement n accumulateurs d'eau chaude séparés avec de l'eau à un niveau de température variable, et pour la récupération de l'énergie, l'eau des n accumulateurs d'eau chaude est respectivement conduite à travers un parmi n évaporateurs montés en série du coté du produit réfrigérant d'un moteur thermique entraîné avec du dioxyde de carbone, où chaque fois, les valeurs de la température de l'eau dans les n refroidisseurs à gaz de la pompe à chaleur et également dans les n évaporateurs du moteur thermique sont ajustées de manière ciblée le long du trajet de l'écoulement dans ces appareils aux différences de température nécessaires pour le transport de la chaleur.
  12. Utilisation de la pompe à chaleur selon la revendication 1 pour le stockage d'énergie, où la pompe à chaleur présente n refroidisseurs de gaz qui, à leur tour, alimentent n utilisateurs de chaleur à différents niveaux de température.
  13. Utilisation de la pompe à chaleur selon la revendication 1 pour le chauffage de fluides pour des processus technologiques, le chauffage de l'eau, le chauffage ou des combinaisons au choix des utilisations avec, chaque fois, des valeurs souhaitées différentes pour les températures de départ d'eau chaude, par le déroulement de l'intervention de boucles individuelles d'après le procédé selon les revendications 3, ainsi que 6 à 11.
EP09736109.1A 2008-09-10 2009-08-28 Pompe à chaleur haute température et son procédé de réglage Active EP2321589B1 (fr)

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 (fr) 2008-09-10 2009-08-28 Pompe à chaleur haute température et son procédé de réglage

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EP2321589A1 EP2321589A1 (fr) 2011-05-18
EP2321589B1 true EP2321589B1 (fr) 2015-08-26

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DE (1) DE102008046620B4 (fr)
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WO2024078669A1 (fr) 2022-10-14 2024-04-18 Lübbers FTS GmbH Dispositif de pompe à chaleur pour la génération économe en énergie d'une chaleur de traitement, dispositif de séchage permettant de sécher un matériau devant être séché, et procédé de fonctionnement d'un dispositif de pompe à chaleur

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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
DE102022121699A1 (de) 2022-08-26 2024-02-29 Konvekta Aktiengesellschaft Wärmepumpenanlage mit mehrstufiger Wärmeübertragung und Verfahren dazu

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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

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WO2023036386A1 (fr) 2021-09-13 2023-03-16 Lübbers Anlagen- und Umwelttechnik GmbH Dispositif de séchage destiné à fournir un gaz de traitement pour une installation de séchage
DE102021123631A1 (de) 2021-09-13 2023-03-16 Lübbers Anlagen- und Umwelttechnik GmbH Trocknungsvorrichtung zum Bereitstellen eines Prozessgases für eine Trockneranlage
WO2024078669A1 (fr) 2022-10-14 2024-04-18 Lübbers FTS GmbH Dispositif de pompe à chaleur pour la génération économe en énergie d'une chaleur de traitement, dispositif de séchage permettant de sécher un matériau devant être séché, et procédé de fonctionnement d'un dispositif de pompe à chaleur
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

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WO2010028622A4 (fr) 2010-05-14
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DE102008046620B4 (de) 2011-06-16
WO2010028622A1 (fr) 2010-03-18

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