EP0969255A2 - Installation avec pompe à chaleur et accumulateur - Google Patents

Installation avec pompe à chaleur et accumulateur Download PDF

Info

Publication number
EP0969255A2
EP0969255A2 EP99111775A EP99111775A EP0969255A2 EP 0969255 A2 EP0969255 A2 EP 0969255A2 EP 99111775 A EP99111775 A EP 99111775A EP 99111775 A EP99111775 A EP 99111775A EP 0969255 A2 EP0969255 A2 EP 0969255A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
temperature
temperature heat
riser pipe
storage
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
Application number
EP99111775A
Other languages
German (de)
English (en)
Other versions
EP0969255B1 (fr
EP0969255A3 (fr
Inventor
Jürgen Köhler
Nicholas Lembke
Wilhelm Tegethoff
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.)
Konvecta AG
Original Assignee
Konvecta AG
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
Priority claimed from DE1998129334 external-priority patent/DE19829334C1/de
Application filed by Konvecta AG filed Critical Konvecta AG
Publication of EP0969255A2 publication Critical patent/EP0969255A2/fr
Publication of EP0969255A3 publication Critical patent/EP0969255A3/fr
Application granted granted Critical
Publication of EP0969255B1 publication Critical patent/EP0969255B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F24H9/00—Details
    • F24H9/0005—Details for water heaters
    • F24H9/001—Guiding means
    • F24H9/0015—Guiding means in water channels
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/0005—Details for water heaters
    • F24H9/001—Guiding means
    • F24H9/0015—Guiding means in water channels
    • F24H9/0021—Sleeves surrounding heating elements or heating pipes, e.g. pipes filled with heat transfer fluid, for guiding heated liquid
    • 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

Definitions

  • the invention relates to a system with a heat pump, a compressor, a high temperature heat exchanger, an expansion device and a low-temperature heat exchanger which is in a circle with each other connected and flowed through by work equipment, and with one containing a storage fluid temperature-stratified storage, in its bottom Area of high temperature heat exchangers of the heat pump is arranged.
  • Such a system is, for example, from the prospectus of Blomberg-Vertriebsgesellschaft mbH, 59229 Ahlen: "WARM WATER HEAT PUMPS and HOT WATER STORAGE", 3rd ed., 2/95, known.
  • High-temperature heat exchangers as smooth-tube heat exchangers educated.
  • finned tubes to the Heat transfer from high temperature heat exchanger to To improve storage fluid.
  • said storage fluid it is usually used water or plain heating water.
  • From CH-PS 524 115 is a water heater Generation and storage of hot water with an in lower part of the with a hot water and a Cold water connection equipped container within a Riser arranged heating unit known.
  • a water heater of the last type mentioned Generation and storage of hot water is also out known from DE 31 37 146 C2.
  • the water heater is the one that receives the heating unit Housing part of the riser pipe towards the inside of the container closed, the cold water supply to the tank in on himself known with a stop device for equipped with a cleaning hose that Cold water supply to the tank in the flow direction of the Water behind the cleaning hose connection with a Bypass line equipped in the housing for the Heating unit opens, a locking device in the Cold water supply between the tank and the connection the bypass line to the cold water supply line, and on the discharge side of the riser pipe inside the container a connecting device for connecting a Cleaning hose provided that the inside of the riser pipe opposite the interior of the container when connected Disconnect the cleaning hose.
  • Heat pumps especially with carbon dioxide as Work equipment can work according to the instantaneous water heater principle are used in which the fluid to be heated, especially water that is heated the moment it is heated is needed.
  • the heated one Store water in a suitable storage tank.
  • Layered memories are known from solar energy technology. These strata stores have an internal one Heat exchanger on the in a flow tank Riser pipe is installed. Such a stratified storage is from the prospectus of Solvis Energysysteme GmbH & Co. KG., 38122 Braunschweig, date of issue: March 25, 1997: "Stratos Integral: hot water and heating support in one Device ", pages 6 and 7, known.
  • the internal Heat exchanger is there to heat the energy of the heat transfer fluid coming to the solar collector Surrender memory.
  • the invention has for its object a system of to create a high Has a performance figure, which is to be heated Storage fluid with a high temperature heat exchanger leaves the highest possible usable temperature, the High temperature heat exchanger is compact and has a high heat transfer capacity, and wherein to drive the volume flow of the to be heated Storage fluid mechanical drive means, such as a pump, are unnecessary.
  • the high-temperature heat exchanger can Cross-countercurrent heat exchanger.
  • the high temperature heat exchanger can be opened in an underside, bell-shaped container can be provided.
  • the said The container can also be closed on the underside.
  • the storage fluid to be heated comes from the lower - i.e. bottom area of the temperature-stratified storage and the heated storage fluid is removed from it
  • the upper area of the memory is layered again.
  • the Plant of the high-temperature heat exchanger according to the invention is designed as a finned tube bundle heat exchanger.
  • Such finned tube bundle heat exchanger can in advantageously small volume, i.e. compact be dimensioned or designed to be a corresponding to realize high heat transfer capacity.
  • the Fins of such a finned tube bundle heat exchanger cause advantageously in flowing, too heating storage fluid only a relatively small Pressure drop so that the thermosiphonic drive does not is disturbed.
  • it is important that the Volume flow of the storage fluid to be heated is not too rises sharply, otherwise the heat to be warmed up Storage fluid not to the necessary useful or Storage tank temperature warmed up.
  • the thermosiphonic volume flow of the to be heated Storage fluids must be large enough to hold the working fluid the carbon dioxide forming the heat pump is sufficiently deep cool down.
  • the riser pipe preferably has one such a clear internal cross-section and such axial length dimension that its thermosiphonic Flow pressure drop a volume flow with lower High temperature heat exchanger outlet temperature of the Heat pump drive means and with high Outlet temperature of the storage fluid to be heated on Has riser pipe outlet of the riser pipe. This will a correspondingly high storage temperature and a high one Achievement figure achieved.
  • thermosiphonic drive and for material saving Increase in countercurrent or Cross-counterflow heat transfer area between the Carbon dioxide from the heat pump and the one to be heated
  • Storage fluid in the storage connected to the heat pump can the compressor of the heat pump by means of a Connection line with the high-temperature heat exchanger be connected, which extends axially from the riser pipe outlet the riser pipe provided in the store extends downwards.
  • the connecting line is coaxial the riser pipe extends.
  • the pipe coil can in the bottom area of the Storage below the high temperature heat exchanger and be arranged below the container in the memory.
  • the Pipe coil can be in at least one level be arranged at least to the bottom of the memory is provided approximately in parallel.
  • the said snake can also be arranged inside the container.
  • a typical application or operating case of plant according to the invention is the heating of drinking water, the water in the temperature-stratified storage tank System in the initial state a homogeneous temperature of e.g. 15 ° C.
  • the heat pump containing carbon dioxide will be in the store located water with the help of the high temperature heat exchanger warmed up. Because of this warming it experiences this Water has a thermosiphonic buoyancy and flows through the riser pipe provided in the storage in the top Storage area. Here it forms due to the low Density compared to the colder storage water a warm one Layer of water. Without significant mixing of the warm water with the cold water underneath the memory is gradually heated up until finally the warm water layer also covers the lower part of the Memory reached.
  • a control device may be provided.
  • This control device is, for example, a valve with which it is possible to regulate the volume flow in the riser pipe in such a way that, regardless of the state of charge of the accumulator and / or regardless of the operating state of the heat pump at the riser pipe outlet, an at least approximately constant temperature of the accumulator fluid is established .
  • Fig. 1 shows a graphical representation of the functional relationship between the temperature T and the enthalpy H in the high-temperature heat exchanger of a heat pump with a conventional refrigerant or working fluid, which is illustrated by the line 10, compared to carbon dioxide as a working fluid the dashed line 12 is shown in the drawing.
  • the reference number 14 in FIG. 1 denotes the functional relationship between the temperature T and the enthalpy H of the fluid to be heated. It can be seen from FIG. 1 that - apart from the desuperheating and supercooling section - there is a largely constant condensation temperature T K in the high-temperature heat exchanger of a heat pump with a conventional refrigerant or working medium.
  • This condensation temperature T K is clearly linked to the condensation pressure via the vapor pressure relationship.
  • the dashed line 12 shows, there is a continuous decrease in temperature, i.e. temperature sliding, of the carbon dioxide gas.
  • the temperature of the working or useful fluid to be heated increases linearly proportionally with the enthalpy H, which is illustrated in FIG. 1 by line 14.
  • the special advantages of carbon dioxide compared to conventional refrigerants are their high environmental compatibility.
  • higher performance figures can be achieved than with conventional compression heat pumps. With fluid temperatures of over 65 ° C to be achieved - in contrast to carbon dioxide - conventional refrigerants can no longer be used sensibly.
  • thermodynamically favorable for conventional refrigerants to heat the fluid to be heated with a low temperature glide since in this case the temperature profile of the fluid to be heated better matches the largely constant temperature profile of the condensed one conventional refrigerant. Because of the high temperature glide of carbon dioxide, a high temperature glide of the fluid to be heated is thermodynamically favorable, as has already been stated.
  • the heat pump 18 has a compressor 22, one High temperature heat exchanger 24, one Expansion device 26 and a low temperature heat exchanger 28 on.
  • the compressor 22, the High temperature heat exchanger 24, the Expansion device 26 and the low-temperature heat exchanger 28 are in a circle with each other connected and flowed through by a work equipment in which it is carbon dioxide.
  • the high temperature heat exchanger 24 of the heat pump 18 is arranged in the bottom region 30 of the memory 20.
  • the memory 20 is filled with a storage fluid 32, he has an undrawn inlet and outlet for the Storage fluid 32 on.
  • the one in the bottom area 30 of the memory 20 provided low temperature heat exchanger 24 is e.g. in a bell-shaped container 34 open on the underside arranged and as a countercurrent heat exchanger, preferably as a cross-counterflow heat exchanger.
  • To the Container 34 encloses the flow on the upper side Riser pipe 36, which is connected to a riser pipe section 38 extends to the upper region 40 of the memory 20.
  • a temperature stratified Memory i.e. the heated storage fluid 32 is in the Riser pipe 36 transported thermosiphonically upwards.
  • the heated storage fluid 32 forms due to its relative low density compared to that at the bottom region 30 located colder storage fluid 32 in the top Area 40 from a warm storage fluid layer. Without significant mixing of the warm with the cold Storage fluid 32 becomes storage fluid 32 in storage 20 gradually warmed from top to bottom until finally the warm storage fluid 32 also the bottom area 30 of the memory 20 reached.
  • FIG. 3 shows a preferred embodiment of the memory 20 in one of FIG. 2 similar schematic Sectional view.
  • the high temperature heat exchanger 24 is here as a finned tube bundle heat exchanger 42 trained as he also in Fig. 4 in a perspective representation is drawn.
  • Such Finned tube bundle heat exchangers are known per se that this need not be discussed in more detail.
  • High temperature heat exchanger 24 is by means of a Connection line 44 with the compressor 22 (see FIG. 2) connected.
  • This connecting line 44 extends from Riser outlet 38 axially, preferably coaxially, through the Riser pipe 36 down into the container 34 and is there to the high-temperature heat exchanger 24 connected.
  • the high temperature heat exchanger 24 is with the expansion device 26 (see FIG. 2) by means of a Return line 46 connected - as can be seen in Fig. 3 is - has a coil 48.
  • This coil 48 is shown in Fig. 3 in a side view simply as a line and underneath in a top or bottom view as Snake line clarified.
  • the coil 48 is at this training in the bottom region 30 of the memory 20 below the high temperature heat exchanger 24 and below the bell-shaped, open on the underside Container 34 arranged.
  • the pipe coil 48 can, for example. also be provided in the container 34.
  • Fig. 5 illustrates in a block or sectional view schematically an embodiment of the system 16, which has a heat pump 18 and a memory 20.
  • the Heat pump 18 has a compressor 22, one High temperature heat exchanger 24, one Expansion device 26 and a low temperature heat exchanger 28 on.
  • the compressor 22, the High temperature heat exchanger 24, the Expansion device 26 and the low-temperature heat exchanger 28 are in a circle with each other connected and by carbon dioxide as a working tool flowed through.
  • the high temperature heat exchanger 24 of the heat pump 18 is in the bottom area 30 of the storage 20 of the system 16 arranged.
  • the memory 20 is provided with a storage fluid 32 filled, it has an undrawn inlet and outlet for the storage fluid 32.
  • the one in the bottom area 30 of the memory 20 provided high temperature heat exchanger 24 is in one Open, bell-shaped container 34 arranged on the underside and dimensioned as a counterflow heat exchanger. This is preferably a so-called Cross-counterflow heat exchanger.
  • a riser pipe is connected to the top of the container 34 36 on that with a riser outlet 38 to area 40 of the memory 20 extends.
  • the storage fluid 32 filled storage 20 of the system 16 is a temperature stratified Storage, in which the heated storage fluid 32 in Riser pipe 36 is transported thermosphonically upwards.
  • the heated storage fluid 32 forms due to its relatively low density compared to that in the bottom Area 30 of colder storage fluid 32 in the top area 40 of memory 20 is a warm one Storage fluid layer. Without significant mixing the warm with the cold storage fluid 32 will Storage fluid 32 in the storage gradually from above heated below until finally the warm storage fluid 32 also the bottom region 30 of the memory 20 reached.
  • a control device 50 provided, which can be a valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP99111775A 1998-07-01 1999-06-18 Installation avec pompe à chaleur et accumulateur Expired - Lifetime EP0969255B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE1998129334 DE19829334C1 (de) 1998-07-01 1998-07-01 Anlage mit einer Wärmepumpe und einem Speicher
DE19829334 1998-07-01
DE19925827 1999-06-07
DE19925827A DE19925827C1 (de) 1998-07-01 1999-06-07 Anlage mit einer Wärmepumpe und einem Speicher

Publications (3)

Publication Number Publication Date
EP0969255A2 true EP0969255A2 (fr) 2000-01-05
EP0969255A3 EP0969255A3 (fr) 2002-07-10
EP0969255B1 EP0969255B1 (fr) 2004-09-15

Family

ID=26047145

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99111775A Expired - Lifetime EP0969255B1 (fr) 1998-07-01 1999-06-18 Installation avec pompe à chaleur et accumulateur

Country Status (3)

Country Link
EP (1) EP0969255B1 (fr)
AT (1) ATE276496T1 (fr)
DE (1) DE19925827C1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10161254A1 (de) * 2001-12-13 2003-07-03 Konvekta Ag Klimatisierungseinrichtung für ein Fahrzeug
EP1431674A1 (fr) * 2002-12-10 2004-06-23 Matsushita Electric Industrial Co., Ltd. Chauffe-eau comprenant un appareil d'adoucissement d'eau
EP1865266A1 (fr) * 2006-06-08 2007-12-12 Erwin Dietz Echangeur de chaleur, spécialement pour chauffer l'eau sanitaire
WO2012020404A3 (fr) * 2010-08-09 2012-12-06 Zvi Shtilerman Appareil et procédé de chauffage d'eau
CN105546819A (zh) * 2016-01-31 2016-05-04 佛山光腾新能源股份有限公司 一种使用二级换热器的热泵机组

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009052559A1 (de) * 2009-11-10 2011-05-12 Markus Kroll Vorrichtung und Verfahren zur Wärmespeicherung und Wärmebereitstellung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH524115A (fr) 1971-05-24 1972-06-15 Cipag S A Appareil chauffe-eau à accumulation
DE3137146A1 (de) 1981-09-18 1983-04-14 Eureka, 4407 Emsdetten "kessel zur erzeugung und speicherung von heissem wasser"

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH289319A (de) * 1953-02-20 1953-03-15 Uhlmann Geb Heisswasserspeicher.
FR1086317A (fr) * 1953-07-06 1955-02-11 Perfectionnement aux chauffe-eau électriques par accumulation
GB1544804A (en) * 1977-05-02 1979-04-25 Commercial Refrigeration Ltd Apparatus for and methods of transferring heat between bodies of fluid or other substance
DE2903250C2 (de) * 1979-01-29 1983-10-20 Manfred 4407 Emsdetten Drieling Kessel zum Erhitzen und Speichern von Wasser
FI915035A7 (fi) * 1991-10-25 1993-04-26 Hannu Koskela Foerfarande och anordning foer uppvaermning av vatten eller naogon annan vaetska
DE4301723C2 (de) * 1992-01-24 1995-03-16 Solar Diamant Syst Warmwasserspeicher
DE4315924A1 (de) * 1993-05-12 1994-11-17 Forschungszentrum Fuer Kaeltet Kälteträger für Kältemaschinen oder Wärmepumpen
DE19542076A1 (de) * 1995-11-11 1997-05-15 Solar Diamant Systemtechnik Un Warmwasserspeicher, insbesondere für Brauchwasser

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH524115A (fr) 1971-05-24 1972-06-15 Cipag S A Appareil chauffe-eau à accumulation
DE3137146A1 (de) 1981-09-18 1983-04-14 Eureka, 4407 Emsdetten "kessel zur erzeugung und speicherung von heissem wasser"

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10161254A1 (de) * 2001-12-13 2003-07-03 Konvekta Ag Klimatisierungseinrichtung für ein Fahrzeug
US6708513B2 (en) 2001-12-13 2004-03-23 Konvekta Ag CO2-module for cooling and heating
EP1431674A1 (fr) * 2002-12-10 2004-06-23 Matsushita Electric Industrial Co., Ltd. Chauffe-eau comprenant un appareil d'adoucissement d'eau
EP1865266A1 (fr) * 2006-06-08 2007-12-12 Erwin Dietz Echangeur de chaleur, spécialement pour chauffer l'eau sanitaire
WO2012020404A3 (fr) * 2010-08-09 2012-12-06 Zvi Shtilerman Appareil et procédé de chauffage d'eau
CN103124880A (zh) * 2010-08-09 2013-05-29 兹维·施基勒尔曼 水加热设备及方法
US20130161404A1 (en) * 2010-08-09 2013-06-27 Zvi Shtilerman Apparatus and method for heating water
AU2011288113B2 (en) * 2010-08-09 2014-05-08 Zvi Shtilerman Apparatus and method for heating water
CN105546819A (zh) * 2016-01-31 2016-05-04 佛山光腾新能源股份有限公司 一种使用二级换热器的热泵机组
CN105546819B (zh) * 2016-01-31 2018-05-25 佛山光腾新能源股份有限公司 一种使用二级换热器的热泵机组

Also Published As

Publication number Publication date
EP0969255B1 (fr) 2004-09-15
ATE276496T1 (de) 2004-10-15
EP0969255A3 (fr) 2002-07-10
DE19925827C1 (de) 2001-01-18

Similar Documents

Publication Publication Date Title
DE19955339B4 (de) Heißwasserversorgungssystem
DE60111448T2 (de) Warmwasserbereitstellungsvorrichtung mit Wärmepumpenkreislauf
DE19500867A1 (de) Verfahren und Vorrichtung zum Betreiben eines Kälteerzeugungssystems
DE19500866A1 (de) Verfahren und Vorrichtung zum Betreiben eines Kälteerzeugssystems, gekennzeichnet durch die Steuerung von Motorkühlmittel
DE3422390A1 (de) Kaelteerzeugungssytem
DE2745938A1 (de) Verfahren und vorrichtung zur rueckgewinnung von waerme aus kaelte- oder klimatisierungssystemen
DE202010015153U1 (de) In einem natürlichen Wärmekörper angeordneter stehender Fluidwärmeaustauscher
DE19500865A1 (de) Verfahren und Vorrichtung zum Betreiben eines Kälteerzeugungssystems, gekennzeichnet durch die Steuerung des Maximalbetriebsdrucks
DE2609489A1 (de) Waermepumpanlage
DE102010003915B4 (de) Kälteanlage mit Wärmerückgewinnung und Verfahren zum Betreiben der Kälteanlage
DE29909871U1 (de) Wärmeaustauscher, insbesondere Ölkühler
EP0969255A2 (fr) Installation avec pompe à chaleur et accumulateur
DE10158104B4 (de) Wärmemanagementvorrichtung für ein Kraftfahrzeug
DE19829334C1 (de) Anlage mit einer Wärmepumpe und einem Speicher
DE102018109577B3 (de) Hybrid-Wärmepumpe mit Kompressions- und Adsorptionskreislauf, sowie Verfahren zumBetrieb und Verwendung
EP0699878B1 (fr) Chauffe-eau à haute rendement pour chauffer et accumuler de l'eau sanitaire et de l'eau de chauffage
DE10012197A1 (de) Thermomanagement für ein Kraftfahrzeug mit einem Kühlmittelkreislauf und einer Klimaanlage
EP2199692A2 (fr) Centrale de chauffage compacte
DE10000352A1 (de) Schichtpufferspeicher mit selbstregelndem Wärmetauscher und Schichtbeladeeinrichtung
WO2010139580A2 (fr) Chauffage par pompe à chaleur, à mélangeur de prélèvement
DE3105796A1 (de) "waermepumpe"
DE10019302A1 (de) Wärmepumpe zur Heizungs- und Brauchwassererwärmung
DE60125146T2 (de) Wärmetauscher für Klimaanlage
DE202004009559U1 (de) Wärmetauscher
DE3308447A1 (de) Vorrichtung zur warmwassererzeugung

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 CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20021212

AKX Designation fees paid

Designated state(s): AT CH FR GB IT LI

REG Reference to a national code

Ref country code: DE

Ref legal event code: 8566

17Q First examination report despatched

Effective date: 20030521

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT CH FR GB IT LI

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: FIAMMENGHI-FIAMMENGHI

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20050110

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050618

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050618

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050630

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050630

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

ET Fr: translation filed
26N No opposition filed

Effective date: 20050616

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20050618

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20090618

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20090627

Year of fee payment: 11

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100618

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100630